JP4384368B2

JP4384368B2 - Hermetic rotary compressor and refrigeration / air conditioner

Info

Publication number: JP4384368B2
Application number: JP2001046403A
Authority: JP
Inventors: 雄幸野; 弘勝香曽我部; 功早瀬; 明彦石山
Original assignee: Hitachi Ltd
Current assignee: Hitachi Ltd
Priority date: 2001-02-22
Filing date: 2001-02-22
Publication date: 2009-12-16
Anticipated expiration: 2021-02-22
Also published as: JP2002250292A

Description

【０００１】
【発明の属する技術分野】
本発明は、密閉型回転圧縮機及び冷凍・空調装置に係り、特に、密閉容器内を吐出圧力より低い圧力とする密閉型回転圧縮機及び冷凍・空調装置に好適なものである。
【０００２】
【従来の技術】
従来、冷蔵庫、冷凍機等の冷凍装置や、ルームエアコン、パッケージ形エアコン等の空調装置等の冷凍・空調装置に用いられているロータリ圧縮機は、密閉容器内に固定子及び回転子を有する電動要素とこの電動要素によって駆動される圧縮要素とが収納され、圧縮要素を構成する駆動軸の偏心部に自転自在に嵌合されたローラが駆動軸の回転によってシリンダ内を偏心回転運動し、ローラに押圧されたベーンによってシリンダ内を吸入室と圧縮室に仕切り、ローラの回転に伴って吸入パイプより吸入室に吸入された冷媒ガスが圧縮室で圧縮され、圧縮された冷媒ガスが密閉容器内に吐出され、さらに吐出パイプより外部の冷凍サイクルに吐出されるように構成されている。このように構成されたロータリ圧縮機はローラに押圧するベーンの背圧を高圧とする為に密閉容器内を吐出圧力とする場合が多い（従来技術１）。
【０００３】
また、密閉容器内を吸入圧力としたロータリ圧縮機として、例えば特開平８−２４７０６２号公報（従来技術２）に示すものが案出されている。係るロータリ圧縮機は、密閉ケース内に吸入ガスを吸込む低圧タイプとなっている。そして、潤滑油は、シャフトの中心下端部に油供給路に沿って設けられた羽根ポンプにより送り出され、クランク室内、主軸受、副軸受等の各摺動部に供給されると共に、シリンダの吸込側にはクランク室と連通する連通路によって潤滑油が供給されるようになっている。また、シャフトの中心部に設けられた油供給路の潤滑油中に発泡した冷媒ガスは、油供給路から延長して形成されたガス抜き孔から上方に排出されるようになっている。更には、圧縮室からローラ内に漏れ込んだ高圧の冷媒ガスは、軸受摺動部に進入しないように、クランク室とシリンダの吸込側とを結ぶ連通路、あるいはクランク室と密閉容器内とを連通するガス排出路から排出されるようになっている。
【０００４】
【発明が解決しようとする課題】
しかし、従来技術１のロータリ圧縮機では、密閉容器内を高温、高圧の吐出圧力にしているので、ローラの内面から吸入室内に差圧によって漏れ込む油が過剰となり加熱損失等による圧縮機の性能低下や、電動要素のコイル温度上昇による信頼性及びモータ効率の低下を招くものであった。また、圧縮機を断続運転する場合、圧縮機停止時に密閉容器内の高温、高圧のガスが蒸発器内に逆流し、蒸発器の温度を上昇させ、冷凍・空調システムの性能を低下させる断続ロスを招くものであった。さらに、地球温暖化防止の観点から可燃性を有する自然系冷媒を使用する場合、冷凍サイクル内の冷媒使用量を少なくすることが望ましいが、油の雰囲気圧力が高いほど油中に溶解する冷媒量が増加するので、密閉容器内圧力が高圧の場合には冷媒使用量が多くなってしまうと共に、軸受等での発泡現象が起こり易く信頼性の低下を招くものであった。しかも、密閉容器の耐圧を高くする必要があるため、密閉容器を厚肉化する必要があり、重量の重くなってしまうものであった。
【０００５】
一方、従来技術２のロータリ圧縮機では、圧縮室からクランク室に漏れ込んだ高圧の冷媒ガスは、クランク室とシリンダの吸込側を結ぶ連通路から排出される場合には、常にクランク室と吸込室が連通しているので、吸込室に油が過剰に供給される問題がある。また、クランク室と密閉容器内を連通するガス排出路から排出される場合には、遠心力によりガス排出路から冷媒ガスが排出される際にクランク室内の潤滑油も一緒に排出されてしまうおそれがある。これにより、クランク室内、主軸受、副軸受等の各摺動部への給油量が不足し潤滑不良を起こすおそれがある。
【０００６】
本発明の目的は、密閉容器内が吐出圧力より低い圧力であっても、軸受摺動部に形成された給油溝に発生する冷媒ガスを駆動軸の内部に形成された冷媒ガス排出路を通して密閉容器内に排出することができ、確実に軸受摺動部に給油できる高性能で信頼性の高い密閉型回転圧縮機及び冷凍・空調装置を提供することにある。
【０００７】
本発明の別の目的は、密閉容器内が吐出圧力より低い圧力であっても、圧縮室からローラ内面に漏れ込んだ冷媒ガスを給油溝を通る潤滑油と干渉することなく駆動軸の内部に形成された冷媒ガス排出路を通して密閉容器内に排出することができると共に、軸受摺動部に形成した給油溝で発生する冷媒ガスを前記冷媒ガス排出路を共用して容易に排出することができ、簡単な構成で確実に軸受摺動部に給油できる高性能で信頼性の高い密閉型回転圧縮機を提供することにある。
【０００８】
本発明の別の目的は、密閉容器内が吐出圧力と吸込圧力との中間圧力であっても、軸受摺動部に形成された給油溝に発生する冷媒ガスを駆動軸の内部に形成された冷媒ガス排出路を通して密閉容器内に排出することができ、確実に軸受摺動部に給油できる高性能で信頼性の高い２段圧縮が可能な密閉型回転圧縮機を提供することにある。
【０００９】
【課題を解決するための手段】
上記目的を達成する為に、本発明の密閉型回転圧縮機は、密閉容器内に電動要素とこの電動要素に連結する圧縮要素とを備え、この圧縮要素のシリンダの両端開口を端板で閉塞してシリンダ室を形成し、この端板に有する主軸受及び副軸受で駆動軸の外周を軸支し、この駆動軸に形成された偏心部を内側に嵌合したローラを前記シリンダ室に配置し、前記駆動軸の回転によって前記シリンダ室内で前記ローラを公転運動することにより冷媒ガスを圧縮すると共に、前記駆動軸の回転による給油ポンプ作用によって前記密閉容器内底部に溜まった潤滑油を、前記駆動軸の軸受摺動部に設けられた給油溝を通して当該軸受摺動部に給油する密閉型回転圧縮機において、前記密閉容器内を前記圧縮要素の吐出圧力より低い圧力にし、一側端が前記密閉容器内に連通されかつ他側端が閉鎖された冷媒ガス排出路を駆動軸の内部に形成すると共に、前記冷媒ガス排出路から半径方向外方に延びて前記ローラ内の空隙に連通する冷媒ガス連通路を前記偏心部に形成したものである。
【００１０】
上記別の目的を達成する為に、本発明の密閉型回転圧縮機は、密閉容器内に電動要素とこの電動要素に連結する圧縮要素とを備え、この圧縮要素のシリンダの両端開口を端板で閉塞してシリンダ室を形成し、この端板に有する主軸受及び副軸受で駆動軸の外周を軸支し、この駆動軸に形成された偏心部を内側に嵌合したローラを前記シリンダ室に配置し、前記駆動軸の回転によって前記シリンダ室内で前記ローラを公転運動することにより冷媒ガスを圧縮すると共に、前記駆動軸の回転による給油ポンプ作用によって前記密閉容器内底部に溜まった潤滑油を、前記駆動軸の軸受摺動部に設けられた給油溝を通して当該軸受摺動部に給油する密閉型回転圧縮機において、前記密閉容器内を前記圧縮要素の吐出圧力より低い圧力にし、一側端が前記密閉容器内に連通されかつ他側端が閉鎖された冷媒ガス排出路を駆動軸の内部に形成すると共に、前記冷媒ガス排出路から半径方向外方に延びて前記ローラ内の前記偏心部と前記端板との間の空隙に連通しかつ前記冷媒ガス排出路から半径方向外方に延びて前記給油溝に連通する冷媒ガス連通路を前記偏心部に形成したものである。
【００１１】
上記別の目的を達成する為に、密閉容器内に電動要素とこの電動要素に連結する圧縮要素とを備え、この圧縮要素を低圧用の圧縮要素と高圧用の圧縮要素の二つの圧縮要素で構成し、前記各圧縮要素のシリンダの両端開口を端板で閉塞して前記各圧縮要素のシリンダ室を形成し、この端板に有する主軸受及び副軸受で駆動軸の外周を軸支し、この駆動軸に形成された前記各圧縮要素の偏心部を内側に嵌合したローラを前記各圧縮要素のシリンダ室に配置し、前記駆動軸の回転によって前記シリンダ室内で前記ローラを公転運動することにより冷媒ガスを２段に圧縮すると共に、前記駆動軸の回転による給油ポンプ作用によって前記密閉容器内底部に溜まった潤滑油を、前記駆動軸の軸受摺動部に設けられた給油溝を通して当該軸受摺動部に給油する密閉型回転圧縮機において、前記密閉容器内を前記圧縮要素の吐出圧力と吸込圧力との中間圧力にし、一側端が前記密閉容器内に連通されかつ他側端が閉鎖された冷媒ガス排出路を駆動軸の内部に形成すると共に、前記冷媒ガス排出路から半径方向外方に延びて前記高圧用の圧縮要素の前記ローラ内の空隙に連通する冷媒ガス連通路を前記高圧用の圧縮要素の偏心部に形成したものである。
【００１２】
【発明の実施の形態】
以下、本発明の各実施例を図を用いて説明する。なお、第２実施例以降の実施例においては第１実施例と共通する構成の一部を省略すると共に、重複する説明を省略する。各実施例の図における同一符号は同一物又は相当物を示す。
【００１３】
まず、本発明の第1実施例を図１から図５を用いて説明する。図１は本発明の第１実施例に係る横置き型揺動ピストン形圧縮機の縦断面図、図２は図１のＡ−Ａ断面図、図３は図２の圧縮要素の動作説明図、図４は図1の圧縮機の要部拡大図、図５は図４の駆動軸部のＢ方向矢視図である。
【００１４】
本発明の揺動ピストン形圧縮機は、密閉容器６内に電動要素、圧縮要素及びこの両者を連結する駆動軸４を配置すると共に、この密閉容器６内を吐出圧力より低い吸入圧力としている。電動要素は、固定子７及び回転子５を有している。圧縮要素は、圧縮機構と給油機構とを有している。圧縮機構は、シリンダ１と、このシリンダ１内に回転可能に配置されたピストン８と、シリンダ１の両端開口を閉塞する主軸受２及び副軸受３等よりなっている。給油機構は、シリンダ１の孔部１ｃ、ベーン部８ｂ、吸込流体ダイオード１７、吐出流体ダイオード１８、給油パイプ１９、スパイラル溝２０及び油ポケット２１等よりなっている。
【００１５】
シリンダ１は、その中央部に円筒状内周面１ａを有するシリンダ室を形成しており、その両端開口が端板を構成する主軸受２と副軸受３とで閉塞されている。この主軸受２と副軸受３は、それぞれ中央に軸受部２ａ、３ａを形成しており、駆動軸４を回転可能に支持している。また、この主軸受２と副軸受３は、支持している駆動軸４の回転軸がシリンダ１の円筒状内周面１ａの中心軸と一致する様に、シリンダ１に固定されている。さらに、主軸受２はその外周部が密閉容器６に固定されている。また、偏心部４ａの主軸受側にはスラスト軸受部４ｈが形成されていることにより、その半径方向外方の主軸受２との間に空隙が形成される。なお、この空隙部に位置して油ポケット２１が形成されている。そして、電動要素の回転子５は駆動軸４に固定され、電動要素の固定子７は回転子５と同軸になるように密閉容器６に固定されている。
【００１６】
また、駆動軸４は、シリンダ１の円筒状内周面１ａ内に位置する部分に、偏心部４ａを形成している。この偏心部４ａは、揺動ピストン８のローラ部８ａの円筒状内周面内に、回転可能に嵌入されている。そして、ローラ部８ａは、シリンダ１の円筒状内周面１ａ内に回転可能に収納され、その円筒状外周面とシリンダ１の円筒状内周面１ａとの間の隙間は微少になる様に各部寸法が決められている。
【００１７】
この揺動ピストン８は、そのローラ部８ａの円筒状外周面から径方向突出してベーン部８ｂを一体的に形成している。即ち、シリンダ１は、その円筒状内周面１ａの外側に連通して、円筒状内周面１ａの中心軸と平行な中心軸を持つ円筒孔部１ｂを形成し、さらに、この円筒孔部１ｂの反シリンダ側になる外側に連通して、シリンダ１及び円筒内周面１ａの中心軸と平行な中心軸を持つ別の孔部１ｃを形成している。そして、ベーン部８ｂは円筒孔部１ｂと孔部１ｃとにまたがって挿入されている。
【００１８】
このようなローラ部８ａとベーン部８ｂとを一体的に形成した揺動ピストン８を用いることにより、ローラ部とベーン部とを別体にして当接しながら摺動するようにしたものに比較して、両者の接触による摩耗等の問題を解消することができる。
【００１９】
また、ベーン部８ｂと円筒孔部１ｂとの間には、ベーン部８ｂの平面部に摺動可能に当接する平面部と円筒孔部１ｂの円筒面部に摺動可能に当接する円筒面部とを有する滑動部材９がベーン部８ｂをはさみ込むように組み込まれている。これにより、ベーン部８ｂは、円筒孔部１ｂの中心軸に向かう進退運動と中心軸廻りの揺動運動を行うように、シリンダ１に支持される。このベーン部８ｂの先端部は、孔部１ｃの中で進退運動及び揺動運動を行ない、シリンダ１と接触することはない。
【００２０】
以上の構成の揺動ピストン形圧縮機において、電動要素により駆動軸４が回転すると、揺動ピストン８は駆動軸４の偏心部４ａの回転にとともに図３（ａ）から（ｆ）に示すようにシリンダ１内を揺動を伴う公転運動を行う。
【００２１】
図３（ａ）から（ｆ）は、駆動軸４が６０°ずつ回転した時の揺動ピストン８の運動を示した図である。この図３から明らかなように、ローラ部８ａはベーン部８ｂが常にシリンダ１の円筒孔部１ｂの中心軸方向を向く様に、偏心部４ａの中心軸廻りに若干の角度だけ揺動運動を行いながらその中心が公転運動をする。これにより、ベーン部８ｂはシリンダ１の円筒孔部１ｂの中心軸に向かった進退運動と該中心軸廻りの揺動運動を行うが、ベーン部８ｂとシリンダ１の円筒孔部１ｂとの間の隙間のシールは滑動部材９が挿入されることにより保たれる。そして、シリンダ１、揺動ピストン８、主軸受２、副軸受３及び滑動部材９とにより密閉空間である圧縮室１０（図３斜線部）と吸入空間である吸入室１１が形成され、電動要素による駆動軸４の回転に伴い図３の様にその容積の増減を繰り返す。
【００２２】
図１に戻って、圧縮要素側に位置する密閉容器６の側面を貫通して吸入パイプ１２が密閉容器６内に開口している。この吸入パイプ１２に近接する位置に吸入通路１３が設けられている。この吸入通路１３は吸入室１２に常時連通している。また、この吸入通路１３の吸込側開口は、吸入パイプ１２の開口と偏心して設けられており、油分離機構を形成している。
【００２３】
かかる構成により、冷媒ガスは、密閉容器６に取り付けられた吸入パイプ１２より密閉容器６内に吸込まれ、吸入通路１３を通過した後、吸入室１１に吸込まれ、圧縮室１０の容積の減少と同時に圧縮され、副軸受３に形成された吐出ポート３ｂから副軸受３と吐出カバー１４によって形成される吐出室３ｃへと吐出される。その後、圧縮された冷媒ガスは吐出パイプ１５から密閉容器６外に吐出される。
【００２４】
このように本実施例では特に、吸入パイプ１２を通過した冷媒ガスを一旦、密閉容器６内に吸込む構造としており、密閉容器６内は吐出圧力より低い吸入圧力となる。密閉容器６内を吸入圧力とすることにより以下のような利点がある。
（１）圧縮された高温の冷媒ガスによる電動要素の加熱が少なく、低温の冷媒ガスによって冷却されるため、回転子５、固定子７の温度が低下し、信頼性が向上すると共にモータ効率が向上して性能向上が図れる。
（２）ローラ部８ａ内が吸入圧力となるので、吸入室１２への差圧による過剰な油の供給がなくなり、加熱損失等の低減が図れることにより圧縮機の性能向上が図れる。
（３）フロン等の油と相溶性のある冷媒を用いる場合では、密閉容器６内の圧力が低い為、油中に溶解する冷媒ガスの割合が少なくなり、軸受等での冷媒ガスの発泡現象が起こりにくく、信頼性を向上することができる。また、可燃性を持つ自然系冷媒（例えばイソブタン、プロパン等）を用いる場合では、冷媒使用量が少なくなり、安全性を高めることができる。
（４）密閉容器６の耐圧を低くでき、薄肉・軽量化が図ることができる。
【００２５】
また、本実施例に示した揺動ピストン形圧縮機は、ローラ部８ａとベーン部８ｂとを一体化しているので、ローラとベーンとを別体にしたロータリ圧縮機のようにローラにベーンを押圧するためにベーンに高圧の背圧をかける必要が無く、密閉容器６内を吸入圧力とした構造に適用し易い。
【００２６】
係る本実施例における圧縮機構部の給油機構について具体的に説明する。
【００２７】
駆動軸４の回転により、図３に示すように、ベーン部８ｂが孔部１ｃの中で進退運動し、孔部１ｃの容積が変化する。この容積変化によるポンプ作用で、密閉容器６の底部に貯溜された潤滑油１６は、図１に示すように、吸込流体ダイオード１７から吸引され、図１及び図４の２点鎖線矢印に示すように、吐出流体ダイオード１８、給油パイプ１９を通って、駆動軸４の一側端部まで汲み上げられ、さらに駆動軸４の外周に設けられたスパイラル溝２０を通って副軸受３、偏心部４ａ、主軸受２を潤滑し、再び密閉容器６内へ戻る。ここで、スパイラル溝２０は、主軸受２、副軸受３側に設けても、同一の作用が得られる。
【００２８】
そして、偏心部４ａを潤滑した潤滑油１６の一部は、ローラ部８ａ内に流出し、図３に示すように、吸入室１１とローラ部８ａ内を交互に行き来する主軸受２の端面に設けられた油ポケット２１によって吸入室１１に供給される。即ち、図３（ａ）、（ｂ）の実線矢印に示すように、油ポケット２１がローラ部８ａ内に位置する状態で潤滑油が油ポケット２１に充満され、図３（ｃ）から（ｅ）の実線矢印に示すように、油ポケット２１が吸入室１１内に位置する状態で潤滑油が油ポケット２１から吸入室１１内に供給される。このようにして、差圧に依らずに容積型ポンプの作用で適正量の潤滑油を吸入室１１に供給できるので、加熱損失等を低減できる。ここで、油ポケット２１は、副軸受３の端面側に設けても、同一の作用が得られる。
【００２９】
また、図４の実線矢印に示すように、スパイラル溝２０を通る潤滑油１６から発泡した冷媒ガスと圧縮室１０からローラ部８ａ内に漏れ込んだ高圧の冷媒ガスは、冷媒ガス連通路を構成するガス抜き孔４ｂを通って駆動軸４の内部に形成されたガス排出穴４ｃにより密閉容器６内へと排出される。これにより、駆動軸４の軸受摺動部における冷媒ガスを低減することができ、軸受摺動部の信頼性を向上することができる。特に、ローラ部８ａ内に漏れた冷媒ガスの排出路４ｂ、４ｃと軸受摺動部のスパイラル溝２０とを独立して構成しているので、冷媒ガスの排出と軸受摺動部等の潤滑油供給とが干渉することなく、確実に機能させることができる。ガス排出穴４ｃは、冷媒ガス排出路を構成するものであり、駆動軸４の偏心部４ａの中心部から駆動軸４の軸心に沿って延び、電動要素側の端面に開口している。また、ガス抜き孔４ｂは、ガス排出穴４ｃから偏心部４ａ内を半径方向外方に延びてローラ部８ａ内の空隙及びスパイラル溝２０に連通する独立した連通路で構成されている。また、ガス抜き孔４ｂは、具体的には、偏心部４ａの主軸受側のスラスト軸受部４ｈの外方の隙間に開口すると共に、この反対側の空隙に開口してそれぞれ連通されている。
【００３０】
ここで、ローラ部８ａ内は、圧縮室１０から漏れ込んだ冷媒ガスと偏心部４ａを潤滑した潤滑油１６とが共存しており、駆動軸４の回転による遠心力によって潤滑油と冷媒ガスの密度差から、密度の高い潤滑油が外側に、密度の低い冷媒ガスが内側に位置するようになるので、ほぼ冷媒ガスのみをガス抜き孔４ｂを通して駆動軸４の内部に形成されたガス排出穴４ｃより排出することができ、高圧の冷媒ガスが軸受摺動部に進入することを防止することができる。しかも、この冷媒ガスの排出の際に、内部シールに必要な吸入室１１への油ポケット２１による給油が冷媒ガスにより阻害されることが無く、シリンダ１内への適正な潤滑油供給を実現して内部漏れを抑制できる。
【００３１】
また、ガス抜き孔４ｂは、偏心部４ａの両側面と主軸受２及び副軸受３との間の空隙に連通するように形成しているので、ローラ部８ａ内に漏れた冷媒ガスを偏心部４ａの両側から確実にかつ迅速に排出することができる。
【００３２】
さらに、ガス抜き孔４ｂは、偏心部４ａの一側に形成したスラスト軸受４ｈの外方に形成される偏心部４ａと主軸受２との間の空隙に連通するように形成しているので、ローラ部８ａ内に漏れたスラスト軸受側の冷媒ガスを確実にかつ迅速に排出することができる。
【００３３】
しかも、ガス排出穴４ｃから半径方向外方に延びてローラ部８ａ内の偏心部４ａと主軸受２及び副軸受３との間の空隙に連通しかつガス排出穴４ｃから半径方向外方に延びてスパイラル溝２０に連通するガス抜き孔４ｂを偏心部４ａに形成しているので、圧縮室１０からローラ部８ａ内に漏れ込んだ冷媒ガスとスパイラル溝２０で発生する冷媒ガスとを共通のガス排出穴４ｃを通して容易に排出することができ、簡単な構成で確実に軸受摺動部に給油できる。
【００３４】
また、ガス排出穴４ｃから半径方向外方に延びてローラ部８ａ内の偏心部４ａ、主軸受２及び副軸受３間の空隙に連通するガス抜き孔４ｂと、ガス排出穴４ｃから半径方向外方に延びてスパイラル溝２０に連通するガス抜き孔４ｂとを独立して形成しているので、ローラ部８ａの内面の冷媒ガスとスパイラル溝２０内の潤滑油から発泡した冷媒ガスとを干渉することなくガス排出穴４ｃに抜くことができる。
【００３５】
以上説明したように、本実施例の構成とすることにより、密閉容器６内を吸入圧力とし、圧縮室１０からローラ部８ａ内に漏れ込んだ冷媒ガスを密閉容器６内に排出する排出通路４ｂ、４ｃと軸受摺動部を潤滑する為のスパイラル溝２０とを分離でき、冷媒ガスと潤滑油が干渉することがないので、各摺動部への確実な給油が可能となり、高性能で信頼性の高い揺動ピストン形圧縮機を提供することができる。
【００３６】
次に、本発明の第２実施例を図６及び図７を用いて説明する。図６は本発明の第２実施例の横置き型揺動ピストン形圧縮機の要部縦断面図、図７は図６の駆動軸部のＣ方向矢視図である。
【００３７】
本実施例においては、冷媒ガスの排出通路に関しては第１実施例で述べたものと同じであるが、主に給油通路が異なるものである。以下に本実施例の給油機構について説明する。
【００３８】
第１実施例で述べた同一のポンプ作用により給油パイプ１９を通って供給された潤滑油１６は、駆動軸４の内部（一側端部の中央部）に形成された穴４ｄに流入し、この穴４ｄから駆動軸４の半径方向外方に延びるように形成された油流出孔４ｅを通って、副軸受３側に形成された溝４ｆへ導かれ、さらに主軸受２側に形成されたスパイラル溝２０を通ることにより、副軸受３、偏心部４ａ、主軸受２を潤滑する。ここで、油流出孔４ｅを通る潤滑油１６は駆動軸４の回転による遠心力が加えられるので、給油量が増加し、各摺動部へ安定した潤滑油の供給が可能となる。
【００３９】
以上の構成とすることにより、密閉容器内を吸入圧力とし、圧縮室からローラ部８ａ内に漏れ込んだ冷媒ガスを密閉容器内に排出する排出通路４ｂ、４ｃと軸受摺動部等を潤滑する為の給油通路４ｆ、２０を分離でき、冷媒ガスと潤滑油が干渉することがなく、かつ、潤滑油１６が油流出孔４ｅを通る際に駆動軸４の回転による遠心力を与えられるので、給油量が増加し、各摺動部への確実な給油が可能となり、高性能で信頼性の高い揺動ピストン形圧縮機を提供することができる。
【００４０】
次に、本発明の第３実施例を図８から図１０を用いて説明する。図８は本発明の第３実施例の縦置き型揺動ピストン形圧縮機の縦断面図、図９は図８のＤ−Ｄ断面図、図１０は図８の圧縮機の要部拡大図である。
【００４１】
本実施例の縦置き型揺動ピストン形圧縮機の圧縮動作は、第１実施例の横置き型揺動ピストン形圧縮機と同様であるが、密閉容器６下部に貯溜した潤滑油１６を駆動軸４まで汲み上げるまでの給油構造が主に異なっている。
【００４２】
駆動軸４の下端に装着された給油ピース４ｇは、密閉容器６内の潤滑油１６中に浸っている。各摺動部への給油は、図１０で明らかなように、駆動軸４の回転による遠心ポンプ作用により、密閉容器６の底部に貯溜された潤滑油１６が駆動軸４の穴４ｄより小径の開口を有する給油ピース４ｇより吸引され、駆動軸４に形成された油流出孔４ｅ及びスパイラル溝２０に供給され、各摺動部の潤滑がなされる。
【００４３】
また、スパイラル溝２０を通る潤滑油１６から発泡した冷媒ガスと圧縮室１０からローラ部８ａ内に漏れ込んだ高圧の冷媒ガスは、ガス抜き孔４ｂを通って、駆動軸４の内部に形成されたガス排出穴４ｃに至り、このガス排出穴４ｃを通って駆動軸４の端部から密閉容器６内へと排出される。
【００４４】
縦置き型圧縮機の場合、各摺動部への潤滑油１６の供給方向が重力と逆行するため、給油量が不足して潤滑不良になり易いが、以上の構成にすることにより、潤滑油１６が油流出孔４ｅを通る際に駆動軸４の回転による遠心力を与えられるため給油量が増加し、更にスパイラル溝２０の粘性ポンプ作用によって副軸受３、偏心部４ａ、主軸受２へ供給されるので、縦置き型圧縮機の場合でも各摺動部へ安定した潤滑油１６の供給ができる。
【００４５】
次に、本発明の第４実施例を図１１及び図１２を用いて説明する。図１１は本発明の第４実施例の横置き型２シリンダロータリ圧縮機の縦断面図、図１２は図１１の圧縮機の要部拡大図である。
【００４６】
本実施例においては、シリンダ２２ａ、２２ｂにはそれぞれ中央部に円筒状内周面２２ｃ、２２ｄが形成されており、その両端開口を中間に仕切り板２３を挟んで主軸受２４と副軸受２５とで閉塞している。なお、この仕切り板２３、主軸受２４及び副軸受２５は、シリンダ２２ａ、２２ｂに対する端板を構成するものである。そして、主軸受２４と副軸受２５にはそれぞれ中央に軸受部２４ａ、２５ａが形成されており、駆動軸２６を回転可能に支持している。また、この主軸受２４と副軸受２５は、駆動軸２６の回転軸がシリンダ２２ａ、２２ｂの円筒状内周面２２ｃ、２２ｄの中心軸と一致する様に、それぞれシリンダ２２ａ、２２ｂに固定されている。駆動軸２６には電動要素の回転子５が固定されている。主軸受２４の外周部は密閉容器６に固定されており、密閉容器６には電動要素の固定子７が固定されている。
【００４７】
駆動軸２６には、シリンダ２２ａ、２２ｂの円筒状内周面２２ｃ、２２ｄにあたる部分に偏心部２６ａと２６ｂが形成されている。この偏心部２６ａ、２６ｂの円筒状外周面にはローラ２７ａ、２７ｂの円筒状内周面が回転可能に嵌入されている。ローラ２７ａ、２７ｂの円筒状外周面とシリンダ２２ａ、２２ｂの円筒状内周面２２ｃ、２２ｄとの間の隙間は微少になる様に各部寸法が決められている。また、ローラ２７ａ、２７ｂの円筒状外周面にはベーン２８ａ、２８ｂがばね２９ａ、２９ｂによって押圧されている。シリンダ２２ａ、２２ｂの円筒状内周面２２ｃ、２２ｄの外側にはベーンスロット（図示せず）が形成されており、ベーン２８ａ、２８ｂはこのベーンスロットに挿入されている。この結果、ベーン２８ａ、２８ｂはベーンスロットの中をシリンダ２２ａ、２２ｂの円筒状内周面２２ｃ、２２ｄの中心軸に向かう進退運動を行う。
【００４８】
以上の構成とすることにより、電動要素により駆動軸２６が回転すると、ローラ２７ａ、２７ｂは偏心部２６ａ、２６ｂとともに公転運動を行う。この公転運動により、冷媒ガスは、密閉容器６に取り付けられた吸入パイプ１２より密閉容器６内に吸込まれ、吸入通路１３を通過した後、シリンダ２２ａ、２２ｂに吸込まれ、圧縮室の容積の減少と同時に圧縮されるが、シリンダ２２ａに吸い込まれた冷媒ガスは主軸受２４に形成された吐出ポート３０ａから主軸受２４と吐出カバー３１ａとによって形成される吐出室３２ａへと吐出され、シリンダ２２ｂに吸い込まれた冷媒ガスは副軸受２５に形成された吐出ポート３０ｂから副軸受２５と吐出カバー３１ｂとによって形成される吐出室３２ｂへと吐出される。その後、両吐出室３２ａ、３２ｂに吐出された冷媒ガスは、合流して、密閉容器６に取り付けられた吐出パイプ１５から圧縮機外部に吐出される。
【００４９】
本実施例の密閉容器６内が吸入圧力となるロータリ圧縮機の場合、密閉容器６内を高圧とした場合のようなベーン２８ａ、２８ｂをローラ２７ａ、２７ｂに押圧するための背圧が無くなるので、ばね２９ａ、２９ｂのばね力を強くする等ローラにベーンを押圧する力を強化する必要がある。
【００５０】
係る本実施例の圧縮機構部の給油機構について説明する。図１１及び図１２において、駆動軸２６の回転により、ベーン２８ｂがベーンスロット（図示せず）の中で進退運動し、ばね２９ｂが装着されている空間２２ｅの容積が変化する。この容積変化によるポンプ作用で、密閉容器６の底部に貯溜された潤滑油１６は、流体ダイオード３３から吸引され、給油パイプ１９を通って、駆動軸２６まで汲み上げられ、駆動軸２６の外周に設けられたスパイラル溝２０を通って主軸受２４、副軸受２５、偏心部２６ａ、２６ｂを潤滑し、再び密閉容器内へ戻る。偏心部２６ａ、２６ｂを潤滑した潤滑油１６の一部は、第1実施例で述べた油ポケット方式と同じ要領で吸入室に供給される。ここで、油ポケットは、主軸受２４の端面、副軸受２５の端面、仕切り板２３の端面のいずれに設けても同一の作用を得ることができる。
【００５１】
スパイラル溝２０を通る潤滑油１６から発泡した冷媒ガスと圧縮室からローラ２７ａ、２７ｂ内面に漏れ込んだ高圧の冷媒ガスは、ガス抜き孔３４ａ、３４ｂを通って駆動軸２６の内部に形成されたガス排出穴４ｃにより密閉容器６内へ排出される。ここで、ローラ２７ａ、２７ｂ内は圧縮室１０から漏れ込んだ冷媒ガスと偏心部２６ａ、２６ｂを潤滑した潤滑油１６が共存しており、駆動軸２６の回転による遠心力によって、潤滑油と冷媒ガスの密度差から、密度の高い潤滑油は外側に、密度の低い冷媒ガスが内側に位置するようになるので、ほぼ冷媒ガスのみをガス抜き孔３４ａ、３４ｂを通して駆動軸２６の内部の形成されたガス排出穴４ｃより排出することができ、この場合に内部シールに必要な吸入室への油ポケットによる給油を阻害することが無く内部漏れを抑制できる。
【００５２】
以上の構成とすることにより、圧縮室からローラ２７ａ、２７ｂ内に漏れ込んだ冷媒ガスを密閉容器６内に排出する排出通路３４ａ、３４ｂ、４ｃと軸受等の摺動部を潤滑する為のスパイラル溝２０とを分離でき、冷媒ガスと潤滑油とが干渉することがないので各摺動部への確実な給油が可能となり、高性能で信頼性の高いロータリ圧縮機を提供することができる。
【００５３】
次に、本発明の第５実施例を図１３及び図１４を用いて説明する。図１３は本発明の第５実施例の横置き型揺動ピストン形２段圧縮機の縦断面図、図１４は図１３の圧縮機の要部拡大図である。
【００５４】
本実施例においては、圧縮要素３５は低圧用圧縮要素３５ａと高圧用圧縮要素３５ｂからなっている。各圧縮要素３５ａ、３５ｂのシリンダ１’、１”の両端開口部は、駆動軸２６の軸支持を兼ねた主軸受２４と副軸受２５及び仕切り板２３により閉塞されている。この主軸受２４、副軸受２５及び仕切り板２３はシリンダ１’、１”に対する端板を構成している。本実施例の揺動ピストン形圧縮機の圧縮動作は、第１実施例で述べた揺動ピストン形圧縮機の場合と基本的には同様であるが、主に冷媒ガスの流れが異なる。
【００５５】
冷媒ガスは、密閉容器６に取り付けられた吸入パイプ３６を通って低圧圧縮要素３５ａのシリンダ１’内に入り圧縮される。圧縮された冷媒ガスは、主軸受２４に形成された吐出ポート３０ａを通り、吐出サイレンサ４１を通って密閉容器６内に吐き出される。密閉容器６内に吐き出された冷媒ガスは、吐出パイプ３７から外部にでて中間冷却器３８により放熱して冷やされた後、吸入パイプ３９を通って高圧用圧縮要素３５ｂのシリンダ１”内に入り圧縮される。圧縮された冷媒ガスは、副軸受２５に配設された吐出ポート３０ｂを通って吐出室３２ｂに入り、ここから吐出パイプ４０を通って圧縮機の外部に流出される。
【００５６】
係る本実施例の圧縮機構部の給油機構について説明する。図１３及び図１４において、駆動軸２６の回転により、高圧用圧縮要素３５ｂのベーン部８ｂ”が孔部１ｃの中で進退運動し、孔部１ｃの容積が変化する。この容積変化によるポンプ作用で、密閉容器６の底部に貯溜された潤滑油１６は、流体ダイオード３３から吸引され、給油パイプ１９を通って駆動軸２６まで汲み上げられ、駆動軸２６の外周に設けられたスパイラル溝２０を通って副軸受２５、偏心部２６ａ、２６ｂ、主軸受２４を潤滑し、再び密閉容器６内へ戻る。低圧用圧縮要素３５ａの偏心部２６ａを潤滑した潤滑油１６の一部は、ローラ部８ａ’内と吸入室の差圧により吸入室に供給され、一方、高圧用圧縮要素３５ｂの偏心部２６ｂを潤滑した潤滑油１６の一部は、第１実施例で述べた油ポケット方式と同じ要領で吸入室に供給される。ここで、油ポケットは、副軸受２５の端面、仕切り板２３の端面のいずれに設けても同一の作用を得ることができる。
【００５７】
スパイラル溝２０を通る潤滑油１６から発泡した冷媒ガスはガス抜き孔３４ａ、３４ｂを通って駆動軸２６の内部に形成されたガス排出穴４ｃに導かれ、高圧用圧縮要素３５ｂの圧縮室からローラ部８ａ”内に漏れ込んだ高圧の冷媒ガスはガス抜き孔３４ｂを通ってガス排出穴４ｃに導かれた後、これらの冷媒はガス排出穴４ｃを通って駆動軸２６の一側端部から密閉容器６内へと排出される。
【００５８】
ここで、高圧用圧縮要素３５ｂのローラ部８ａ”内は、圧縮室１０から漏れ込んだ冷媒ガスと偏心部２６ｂを潤滑した潤滑油１６とが共存しており、駆動軸２６の回転による遠心力によって、潤滑油と冷媒ガスの密度差から、密度の高い潤滑油は外側に、密度の低い冷媒ガスが内側に位置するようになるので、ほぼ冷媒ガスのみをガス抜き孔３４ｂを通して駆動軸２６の内部の形成されたガス排出穴４ｃより排出することができ、高圧の冷媒ガスが軸受摺動部に進入することを防止することができる。しかも、この冷媒ガスの排出の際に、内部シールに必要な吸入室への油ポケットによる給油を阻害することが無く、シリンダ内への適正な潤滑油供給を実現して内部漏れを抑制できる。
【００５９】
以上の構成とすることにより、圧縮室からローラ部８ａ”内に漏れ込んだ冷媒ガスを密閉容器６内へ排出する排出通路３４ｂ、４ｃと軸受摺動部を潤滑する為のスパイラル溝２０とを分離でき、冷媒ガスと潤滑油とが干渉することがないので各摺動部への確実な給油が可能となり、高性能で信頼性の高い横置き型揺動ピストン形２段圧縮機を提供することができる。
【００６０】
次に、本発明の第６実施例を図１５を用いて説明する。図１５は本発明の第６実施例の冷凍装置の冷凍サイクル構成図である。この冷凍サイクルは冷凍（冷房）専用のサイクルの例である。
【００６１】
図１５において、冷凍サイクルは、密閉型回転圧縮機４５、凝縮器４２、減圧装置を構成する膨張弁４３、蒸発器４４を配管で接続して形成されている。凝縮器ファン４２ａは凝縮器４２に強制的に送風するものであり、蒸発器ファン４４ａは蒸発器４４に強制的に送風するものである。
【００６２】
係る密閉型回転圧縮機４５を起動することにより、密閉型回転圧縮機４５で圧縮された高温・高圧の作動ガスは、実線矢印で示すように吐出パイプ１５から凝縮器４２に流入して、凝縮器ファン４２ａの送風作用で放熱、液化し、膨張弁４３で絞られ、断熱膨張して低温・低圧となり、蒸発器ファン４４ａの送風作用により蒸発器４４で吸熱、ガス化された後、吸入パイプ１２を経て密閉型回転圧縮機４５に吸入される。そして、密閉型回転圧縮機４５は運転指令及び運転状態検出信号に基づいて断続運転される。
【００６３】
係る冷凍装置は、上述した本発明の密閉型回転圧縮機４５を搭載しているので、エネルギー効率に優れた冷凍システムが得られる。特に、本発明の密閉型回転圧縮機４５は密閉容器内を吐出圧力以下にしているので、断続運転時に高温・高圧の冷媒が蒸発器内に流入する量を少なくでき、断続エネルギーロスを低減できる。
【００６４】
なお、ここでは、単段圧縮機を用いて説明したが、２段圧縮機も搭載でき、冷凍装置だけでなく空調装置にも適用可能である。
【００６５】
【発明の効果】
以上説明したように、本発明によれば、密閉容器内が吐出圧力より低い圧力であっても、軸受摺動部に形成された給油溝に発生する冷媒ガスを駆動軸の内部に形成された冷媒ガス排出路を通して密閉容器内に排出することができ、確実に軸受摺動部に給油できる高性能で信頼性の高い密閉型回転圧縮機及び冷凍・空調装置を提供することができる。
【００６６】
また、本発明によれば、密閉容器内が吐出圧力より低い圧力であっても、圧縮室からローラ内面に漏れ込んだ冷媒ガスを給油溝を通る潤滑油と干渉することなく駆動軸の内部に形成された冷媒ガス排出路を通して密閉容器内に排出することができると共に、軸受摺動部に形成した給油溝で発生する冷媒ガスを前記冷媒ガス排出路を共用して容易に排出することができ、簡単な構成で確実に軸受摺動部に給油できる高性能で信頼性の高い密閉型回転圧縮機を提供することができる。
【００６７】
また、本発明によれば、密閉容器内が吐出圧力と吸込圧力との中間圧力であっても、軸受摺動部に形成された給油溝に発生する冷媒ガスを駆動軸の内部に形成された冷媒ガス排出路を通して密閉容器内に排出することができ、確実に軸受摺動部に給油できる高性能で信頼性の高い２段圧縮が可能な密閉型回転圧縮機を提供することができる。
【図面の簡単な説明】
【図１】本発明の第１実施例に係る横置き型揺動ピストン形圧縮機の縦断面図である。
【図２】図１のＡ−Ａ断面図である。
【図３】図２の圧縮要素の動作説明図である。
【図４】図1の圧縮機の要部拡大図である。
【図５】図４の駆動軸部のＢ方向矢視図である。
【図６】本発明の第２実施例の横置き型揺動ピストン形圧縮機の要部縦断面図である。
【図７】図６の駆動軸部のＣ方向矢視図である。
【図８】本発明の第３実施例の縦置き型揺動ピストン形圧縮機の縦断面図である。
【図９】図８のＤ−Ｄ断面図である。
【図１０】図８の圧縮機の要部拡大図である。
【図１１】本発明の第４実施例の横置き型２シリンダロータリ圧縮機の縦断面図である。
【図１２】図１１の圧縮機の要部拡大図である。
【図１３】本発明の第５実施例の横置き型揺動ピストン形２段圧縮機の縦断面図である。
【図１４】図１３の圧縮機の要部拡大図である。
【図１５】本発明の第６実施例の冷凍装置の冷凍サイクル構成図である。
【符号の説明】
１…シリンダ、１’…シリンダ、１”…シリンダ、１ａ…円筒状内周面、１ｂ…円筒孔部、１ｃ…孔部、２…主軸受、２ａ…軸受部、３…副軸受、３ａ…軸受部、３ｂ…吐出ポート、３ｃ…吐出室、４…駆動軸、４ａ…偏心部、４ｂ…ガス抜き孔、４ｃ…ガス排出穴、４ｄ…穴、４ｅ…油流出孔、４ｆ…溝、４ｇ…給油ピース、５…回転子、６…密閉容器、７…固定子、８…揺動ピストン、８ａ…ローラ部、８ａ’…ローラ部、８ａ”…ローラ部、８ｂ…ベーン部、８ｂ’…ベーン部、８ｂ”…ベーン部、９…滑動部材、１０…圧縮室、１１…吸入室、１２…吸入パイプ、１３…吸入通路、１４…吐出カバー、１５…吐出パイプ、１６…潤滑油、１７…吸込流体ダイオード、１８…吐出流体ダイオード、１９…給油パイプ、２０…スパイラル溝、２１…油ポケット、２２ａ、２２ｂ…シリンダ、２２ｃ、２２ｄ…円筒状内周面、２２ｅ…空間、２３…仕切り板、２４…主軸受、２４ａ…軸受部、２５…副軸受、２５ａ…軸受部、２６…駆動軸、２６ａ、２６ｂ…偏心部、２７ａ、２７ｂ…ローラ、２８ａ、２８ｂ…ベーン、２９ａ、２９ｂ…ばね、３０ａ、３０ｂ…吐出ポート、３１ａ、３１ｂ…吐出カバー、３２ａ、３２ｂ…吐出室、３３…流体ダイオード、３４ａ、３４ｂ…ガス抜き孔、３５…圧縮要素、３５ａ…低圧用圧縮要素、３５ｂ…高圧用圧縮要素、３６…吸入パイプ、３７…吐出パイプ、３８…中間冷却器、３９…吸入パイプ、４０…吐出パイプ、４１…吐出サイレンサ、４２…凝縮器、４２ａ…凝縮器ファン、４３…膨張弁、４４…蒸発器、４４ａ…蒸発器ファン、４５…密閉型回転圧縮機。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a hermetic rotary compressor and a refrigeration / air conditioning apparatus, and is particularly suitable for a hermetic rotary compressor and a refrigeration / air conditioning apparatus that make the inside of a hermetic container lower than the discharge pressure.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, rotary compressors used in refrigeration devices such as refrigerators and refrigerators, and refrigeration and air conditioning devices such as room air conditioners and packaged air conditioners are electrically operated with a stator and a rotor in a hermetically sealed container. An element and a compression element driven by the electric element are housed, and a roller that is rotatably fitted to an eccentric part of a drive shaft that constitutes the compression element rotates eccentrically in the cylinder by the rotation of the drive shaft. The inside of the cylinder is partitioned into a suction chamber and a compression chamber by the vane pressed by the cylinder, and the refrigerant gas sucked into the suction chamber from the suction pipe as the roller rotates is compressed in the compression chamber, and the compressed refrigerant gas is stored in the sealed container. And is further discharged from the discharge pipe to the external refrigeration cycle. The rotary compressor configured as described above often uses a discharge pressure in the hermetic container in order to increase the back pressure of the vane pressed against the roller.
[0003]
Further, as a rotary compressor in which the inside of a sealed container has a suction pressure, for example, the one shown in Japanese Patent Application Laid-Open No. 8-247062 (prior art 2) has been devised. Such a rotary compressor is a low-pressure type that sucks inhaled gas into a sealed case. The lubricating oil is sent out by a blade pump provided along the oil supply path at the center lower end portion of the shaft, and is supplied to each sliding portion such as the crank chamber, the main bearing, and the sub-bearing, and is also sucked into the cylinder. Lubricating oil is supplied to the side through a communication passage communicating with the crank chamber. Further, the refrigerant gas foamed in the lubricating oil in the oil supply path provided at the center of the shaft is discharged upward from a gas vent hole formed extending from the oil supply path. Further, the high-pressure refrigerant gas leaking from the compression chamber into the roller does not enter the bearing sliding portion, and is connected to the communication path connecting the crank chamber and the suction side of the cylinder or between the crank chamber and the sealed container. The gas is discharged from the communicating gas discharge path.
[0004]
[Problems to be solved by the invention]
However, in the rotary compressor of prior art 1, since the inside of the hermetic container is set at a high temperature and high pressure, the oil leaking from the inner surface of the roller into the suction chamber due to the differential pressure becomes excessive, and the performance of the compressor due to heating loss and the like. The reduction and reliability due to the coil temperature increase of the electric element and the reduction of the motor efficiency are caused. Also, when the compressor is operated intermittently, intermittent loss that causes high-temperature and high-pressure gas in the sealed container to flow back into the evaporator when the compressor is stopped, raising the temperature of the evaporator and lowering the performance of the refrigeration / air-conditioning system. Was inviting. Furthermore, when using a flammable natural refrigerant from the viewpoint of preventing global warming, it is desirable to reduce the amount of refrigerant used in the refrigeration cycle, but the amount of refrigerant that dissolves in oil as the atmospheric pressure of the oil increases. Therefore, when the internal pressure of the sealed container is high, the amount of refrigerant used increases, and a foaming phenomenon easily occurs in a bearing or the like, leading to a decrease in reliability. Moreover, since it is necessary to increase the pressure resistance of the sealed container, it is necessary to increase the thickness of the sealed container, which increases the weight.
[0005]
On the other hand, in the rotary compressor of the prior art 2, when the high-pressure refrigerant gas leaked from the compression chamber into the crank chamber is discharged from the communication passage connecting the crank chamber and the suction side of the cylinder, the suction is always performed between the crank chamber and the suction chamber. Since the chambers communicate with each other, there is a problem that oil is excessively supplied to the suction chamber. Further, when the refrigerant gas is discharged from the gas discharge passage communicating with the crank chamber and the sealed container, the lubricating oil in the crank chamber may be discharged together with the refrigerant gas discharged from the gas discharge passage due to centrifugal force. There is. As a result, the amount of oil supplied to the sliding parts such as the crank chamber, the main bearing, and the sub-bearing is insufficient, which may cause poor lubrication.
[0006]
The object of the present invention is to But Pressure lower than discharge pressure Even , Occurs in the oil groove formed in the sliding part of the bearing Refrigerant gas Through the refrigerant gas discharge passage formed inside the drive shaft An object of the present invention is to provide a high-performance and highly reliable hermetic rotary compressor and refrigeration / air-conditioning device that can be discharged into a hermetic container and can reliably supply oil to the bearing sliding portion.
[0007]
Another object of the present invention is to provide a sealed container. But Pressure lower than discharge pressure Even , Refrigerant gas leaking from the compression chamber to the inner surface of the roller Go through the oil groove Without interfering with lubricant Through the refrigerant gas discharge passage formed inside the drive shaft Refrigerant gas generated in the oil groove formed in the bearing sliding part can be discharged into the sealed container. The refrigerant gas It is an object of the present invention to provide a high-performance and highly reliable hermetic rotary compressor that can discharge easily by sharing a discharge path and can reliably supply oil to a bearing sliding portion with a simple configuration.
[0008]
Another object of the present invention is to provide a sealed container. But Intermediate pressure between discharge pressure and suction pressure Even , Occurs in the oil groove formed in the sliding part of the bearing Refrigerant gas Through the refrigerant gas discharge passage formed inside the drive shaft It is an object of the present invention to provide a hermetic rotary compressor that can be discharged into a hermetic container and can reliably supply oil to the bearing sliding portion and can perform two-stage compression with high reliability.
[0009]
[Means for Solving the Problems]
In order to achieve the above object, the present invention Dense The closed rotary compressor includes an electric element and a compression element connected to the electric element in a hermetic container, and both end openings of the cylinder of the compression element are closed with end plates to form a cylinder chamber. Main shaft and sub bearing with drive shaft Outer circumference Is formed on this drive shaft Is Eccentric part The inside Mated to Shi The roller is disposed in the cylinder chamber, the refrigerant gas is compressed by revolving the roller in the cylinder chamber by the rotation of the drive shaft, and the inner bottom portion of the hermetic container by the oil supply pump action by the rotation of the drive shaft Lubricant accumulated in , In the bearing sliding part of the drive shaft The bearing sliding part through the oil groove provided In the hermetic rotary compressor for refueling, the inside of the hermetic container is set to a pressure lower than the discharge pressure of the compression element, One side is Communicate in the sealed container And the other end is closed Refrigerant gas discharge path to drive shaft Inside In addition, a refrigerant gas communication path that extends radially outward from the refrigerant gas discharge path and communicates with a gap in the roller is formed in the eccentric portion.
[0010]
In order to achieve the above another object, the present invention Dense The closed rotary compressor includes an electric element and a compression element connected to the electric element in a hermetic container, and both end openings of the cylinder of the compression element are closed with end plates to form a cylinder chamber. Main shaft and sub bearing with drive shaft Outer circumference Is formed on this drive shaft Is Eccentric part The inside Mated to Shi The roller is disposed in the cylinder chamber, the refrigerant gas is compressed by revolving the roller in the cylinder chamber by the rotation of the drive shaft, and the inner bottom portion of the hermetic container by the oil supply pump action by the rotation of the drive shaft Lubricant accumulated in , In the bearing sliding part of the drive shaft The bearing sliding part through the oil groove provided Refuel Dense In the closed rotary compressor, the inside of the closed container is set to a pressure lower than the discharge pressure of the compression element, One side is Communicate in the sealed container And the other end is closed Refrigerant gas discharge path to drive shaft Inside And extending radially outward from the refrigerant gas discharge path to communicate with a gap between the eccentric portion and the end plate in the roller and radially outward from the refrigerant gas discharge path. The refrigerant gas communication passage communicating with the oil supply groove is formed in the eccentric portion.
[0011]
In order to achieve the above another object, an electric element and a compression element connected to the electric element are provided in a sealed container, and the compression element is divided into two compression elements, a low pressure compression element and a high pressure compression element. A cylinder shaft of each compression element is formed by closing both end openings of the cylinder of each compression element with an end plate, and a drive shaft is formed by a main bearing and a sub-bearing included in the end plate. Outer circumference Is formed on this drive shaft Is The eccentric part of each compression element The inside Mated to Shi The roller is disposed in the cylinder chamber of each compression element, and the revolving motion of the roller in the cylinder chamber by the rotation of the drive shaft compresses the refrigerant gas in two stages, and the oil supply pump by the rotation of the drive shaft The lubricating oil collected at the bottom of the sealed container , In the bearing sliding part of the drive shaft The bearing sliding part through the oil groove provided In the hermetic rotary compressor for refueling, the inside of the sealed container is set to an intermediate pressure between the discharge pressure and the suction pressure of the compression element, One side is Communicate in the sealed container And the other end is closed Refrigerant gas discharge path to drive shaft Inside And a refrigerant gas communication path extending radially outward from the refrigerant gas discharge path and communicating with a gap in the roller of the high pressure compression element is formed in the eccentric portion of the high pressure compression element. Is.
[0012]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings. In the second and subsequent embodiments, a part of the configuration common to the first embodiment is omitted, and a duplicate description is omitted. The same reference numerals in the drawings of the respective embodiments indicate the same or equivalent.
[0013]
First, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view of a horizontally mounted oscillating piston compressor according to a first embodiment of the present invention, FIG. 2 is a sectional view taken along line AA in FIG. 1, and FIG. 4 is an enlarged view of a main part of the compressor of FIG. 1, and FIG. 5 is a view in the direction of arrow B of the drive shaft portion of FIG.
[0014]
In the oscillating piston compressor of the present invention, an electric element, a compression element, and a drive shaft 4 that couples both are arranged in a sealed container 6 and the inside of the sealed container 6 is set to a suction pressure lower than a discharge pressure. The electric element has a stator 7 and a rotor 5. The compression element has a compression mechanism and an oil supply mechanism. The compression mechanism includes a cylinder 1, a piston 8 disposed rotatably in the cylinder 1, a main bearing 2 and a sub-bearing 3 that close both ends of the cylinder 1. The oil supply mechanism includes a hole portion 1c of the cylinder 1, a vane portion 8b, a suction fluid diode 17, a discharge fluid diode 18, an oil supply pipe 19, a spiral groove 20, an oil pocket 21, and the like.
[0015]
The cylinder 1 forms a cylinder chamber having a cylindrical inner peripheral surface 1a at the center thereof, and both end openings are closed by a main bearing 2 and a sub-bearing 3 constituting end plates. The main bearing 2 and the sub-bearing 3 are respectively formed with bearing portions 2a and 3a in the center, and support the drive shaft 4 in a rotatable manner. The main bearing 2 and the sub-bearing 3 are fixed to the cylinder 1 so that the rotating shaft of the driving shaft 4 that is supported coincides with the central axis of the cylindrical inner peripheral surface 1 a of the cylinder 1. Further, the outer periphery of the main bearing 2 is fixed to the sealed container 6. Further, since the thrust bearing portion 4h is formed on the main bearing side of the eccentric portion 4a, a space is formed between the eccentric portion 4a and the main bearing 2 on the radially outer side. An oil pocket 21 is formed in the gap. The electric element rotor 5 is fixed to the drive shaft 4, and the electric element stator 7 is fixed to the hermetic container 6 so as to be coaxial with the rotor 5.
[0016]
In addition, the drive shaft 4 forms an eccentric portion 4 a in a portion located in the cylindrical inner peripheral surface 1 a of the cylinder 1. The eccentric portion 4 a is rotatably fitted in the cylindrical inner peripheral surface of the roller portion 8 a of the swing piston 8. The roller portion 8a is rotatably accommodated in the cylindrical inner peripheral surface 1a of the cylinder 1 so that the gap between the cylindrical outer peripheral surface and the cylindrical inner peripheral surface 1a of the cylinder 1 is very small. The dimensions of each part are determined.
[0017]
The swing piston 8 protrudes in the radial direction from the cylindrical outer peripheral surface of the roller portion 8a to integrally form a vane portion 8b. That is, the cylinder 1 communicates with the outside of the cylindrical inner peripheral surface 1a to form a cylindrical hole 1b having a central axis parallel to the central axis of the cylindrical inner peripheral surface 1a. Another hole 1c having a central axis parallel to the central axis of the cylinder 1 and the cylindrical inner peripheral surface 1a is formed so as to communicate with the outer side of the cylinder 1 and the cylinder inner peripheral surface 1a. The vane portion 8b is inserted across the cylindrical hole portion 1b and the hole portion 1c.
[0018]
By using such a swinging piston 8 in which the roller portion 8a and the vane portion 8b are integrally formed, the roller portion and the vane portion are separated from each other and are slid while being in contact with each other. Thus, problems such as wear due to contact between the two can be solved.
[0019]
Further, between the vane portion 8b and the cylindrical hole portion 1b, there are a flat surface portion that slidably contacts the flat surface portion of the vane portion 8b and a cylindrical surface portion that slidably contacts the cylindrical surface portion of the cylindrical hole portion 1b. A sliding member 9 having the vane portion 8b is incorporated. As a result, the vane portion 8b is supported by the cylinder 1 so as to perform a forward / backward movement toward the central axis of the cylindrical hole portion 1b and a swinging movement around the central axis. The tip of the vane portion 8b performs forward / backward movement and rocking movement in the hole 1c and does not come into contact with the cylinder 1.
[0020]
In the oscillating piston compressor having the above configuration, when the drive shaft 4 is rotated by the electric element, the oscillating piston 8 is rotated with the eccentric portion 4a of the drive shaft 4 as shown in FIGS. In addition, a revolving motion with swinging is performed in the cylinder 1.
[0021]
FIGS. 3A to 3F are views showing the movement of the oscillating piston 8 when the drive shaft 4 is rotated by 60 °. As is apparent from FIG. 3, the roller portion 8a oscillates by a slight angle around the central axis of the eccentric portion 4a so that the vane portion 8b always faces the central axis direction of the cylindrical hole portion 1b of the cylinder 1. The center revolves while performing. As a result, the vane portion 8b performs an advancing / retreating motion toward the central axis of the cylindrical hole portion 1b of the cylinder 1 and a swinging motion around the central axis, but between the vane portion 8b and the cylindrical hole portion 1b of the cylinder 1 The seal of the gap is maintained by inserting the sliding member 9. The cylinder 1, the swinging piston 8, the main bearing 2, the sub bearing 3, and the sliding member 9 form a compression chamber 10 (shaded portion in FIG. 3) that is a sealed space and a suction chamber 11 that is a suction space. As the drive shaft 4 rotates, the volume is repeatedly increased and decreased as shown in FIG.
[0022]
Returning to FIG. 1, the suction pipe 12 opens into the sealed container 6 through the side surface of the sealed container 6 positioned on the compression element side. A suction passage 13 is provided at a position close to the suction pipe 12. The suction passage 13 is always in communication with the suction chamber 12. Further, the suction side opening of the suction passage 13 is provided eccentrically with the opening of the suction pipe 12 to form an oil separation mechanism.
[0023]
With this configuration, the refrigerant gas is sucked into the sealed container 6 from the suction pipe 12 attached to the sealed container 6, passes through the suction passage 13, and then sucked into the suction chamber 11, reducing the volume of the compression chamber 10. At the same time, it is compressed and discharged from a discharge port 3 b formed in the sub-bearing 3 to a discharge chamber 3 c formed by the sub-bearing 3 and the discharge cover 14. Thereafter, the compressed refrigerant gas is discharged out of the sealed container 6 from the discharge pipe 15.
[0024]
Thus, in this embodiment, in particular, the refrigerant gas that has passed through the suction pipe 12 is once sucked into the sealed container 6, and the suction pressure in the sealed container 6 is lower than the discharge pressure. There are the following advantages by using the suction pressure in the sealed container 6.
(1) Since the electric element is less heated by the compressed high-temperature refrigerant gas and is cooled by the low-temperature refrigerant gas, the temperature of the rotor 5 and the stator 7 is lowered, and the reliability is improved and the motor efficiency is improved. Improve performance.
(2) Since the inside of the roller portion 8a becomes the suction pressure, excess oil is not supplied to the suction chamber 12 due to the differential pressure, and the heat loss and the like can be reduced, thereby improving the compressor performance.
(3) When a refrigerant that is compatible with oil such as chlorofluorocarbon is used, since the pressure in the hermetic container 6 is low, the ratio of the refrigerant gas dissolved in the oil decreases, and the refrigerant gas foams in the bearing or the like. Is less likely to occur and reliability can be improved. In addition, when using a flammable natural refrigerant (for example, isobutane, propane, etc.), the amount of refrigerant used is reduced and safety can be improved.
(4) The pressure resistance of the sealed container 6 can be lowered, and the thickness and weight can be reduced.
[0025]
Further, in the swing piston type compressor shown in this embodiment, since the roller portion 8a and the vane portion 8b are integrated, the roller is vaned like a rotary compressor in which the roller and the vane are separated. It is not necessary to apply a high back pressure to the vane in order to press, and it is easy to apply to a structure in which the inside of the sealed container 6 is a suction pressure.
[0026]
The oil supply mechanism of the compression mechanism part in this embodiment will be specifically described.
[0027]
As shown in FIG. 3, the rotation of the drive shaft 4 causes the vane portion 8b to move forward and backward in the hole 1c, and the volume of the hole 1c changes. As shown in FIG. 1, the lubricating oil 16 stored at the bottom of the sealed container 6 by the pump action due to the volume change is sucked from the suction fluid diode 17 and shown by the two-dot chain arrows in FIGS. Are further pumped up to one end of the drive shaft 4 through the discharge fluid diode 18 and the oil supply pipe 19, and further through the spiral groove 20 provided on the outer periphery of the drive shaft 4, to the auxiliary bearing 3, the eccentric portion 4a, The main bearing 2 is lubricated and returned to the sealed container 6 again. Here, even if the spiral groove 20 is provided on the main bearing 2 and auxiliary bearing 3 side, the same action can be obtained.
[0028]
A part of the lubricating oil 16 that has lubricated the eccentric portion 4a flows into the roller portion 8a and, as shown in FIG. 3, reaches the end surface of the main bearing 2 that alternates between the suction chamber 11 and the roller portion 8a. The oil pocket 21 is supplied to the suction chamber 11. That is, as indicated by solid arrows in FIGS. 3A and 3B, the lubricating oil is filled in the oil pocket 21 in a state where the oil pocket 21 is positioned in the roller portion 8a, and from FIG. As indicated by a solid line arrow), lubricating oil is supplied from the oil pocket 21 into the suction chamber 11 in a state where the oil pocket 21 is located in the suction chamber 11. In this way, since an appropriate amount of lubricating oil can be supplied to the suction chamber 11 by the action of the positive displacement pump without depending on the differential pressure, heating loss and the like can be reduced. Here, even if the oil pocket 21 is provided on the end face side of the auxiliary bearing 3, the same action can be obtained.
[0029]
Further, as indicated by solid line arrows in FIG. 4, the refrigerant gas foamed from the lubricating oil 16 passing through the spiral groove 20 and the high-pressure refrigerant gas leaked from the compression chamber 10 into the roller portion 8a constitute a refrigerant gas communication path. The gas is discharged into the sealed container 6 through a gas vent hole 4b formed in the drive shaft 4 through the vent hole 4b. Thereby, the refrigerant gas in the bearing sliding part of the drive shaft 4 can be reduced, and the reliability of the bearing sliding part can be improved. Particularly, since the refrigerant gas discharge paths 4b and 4c leaking into the roller portion 8a and the spiral groove 20 of the bearing sliding portion are configured independently, the refrigerant gas is discharged and the lubricating oil such as the bearing sliding portion is provided. It can function reliably without interference with the supply. The gas discharge hole 4c constitutes a refrigerant gas discharge path, extends from the central portion of the eccentric portion 4a of the drive shaft 4 along the axis of the drive shaft 4, and opens to the end face on the electric element side. Further, the gas vent hole 4b is configured as an independent communication path that extends radially outward in the eccentric part 4a from the gas discharge hole 4c and communicates with the gap in the roller part 8a and the spiral groove 20. Further, the degassing holes 4b are opened to the outer clearance of the thrust bearing portion 4h on the main bearing side of the eccentric portion 4a, and are opened to communicate with the gaps on the opposite side.
[0030]
Here, in the roller portion 8a, the refrigerant gas leaking from the compression chamber 10 and the lubricating oil 16 that lubricates the eccentric portion 4a coexist, and the lubricating oil and the refrigerant gas are separated by the centrifugal force generated by the rotation of the drive shaft 4. Due to the difference in density, the high density lubricating oil is located outside and the low density refrigerant gas is located inside. Therefore, only the refrigerant gas is passed through the vent hole 4b and the gas discharge hole formed in the drive shaft 4 is formed. 4c can be discharged, and high-pressure refrigerant gas can be prevented from entering the bearing sliding portion. Moreover, when the refrigerant gas is discharged, the supply of oil by the oil pocket 21 to the suction chamber 11 necessary for the internal seal is not hindered by the refrigerant gas, and an appropriate lubricating oil supply into the cylinder 1 is realized. Internal leakage can be suppressed.
[0031]
Further, since the gas vent hole 4b is formed so as to communicate with the gap between the both side surfaces of the eccentric portion 4a and the main bearing 2 and the sub bearing 3, the refrigerant gas leaked into the roller portion 8a is removed from the eccentric portion. It is possible to reliably and quickly discharge from both sides of 4a.
[0032]
Further, the vent hole 4b is formed so as to communicate with the gap between the eccentric part 4a formed on the outer side of the thrust bearing 4h formed on one side of the eccentric part 4a and the main bearing 2. The refrigerant gas on the thrust bearing side leaking into the roller portion 8a can be reliably and quickly discharged.
[0033]
Moreover, it extends radially outward from the gas discharge hole 4c, communicates with the gap between the eccentric portion 4a in the roller portion 8a and the main bearing 2 and the sub bearing 3, and extends radially outward from the gas discharge hole 4c. Since the vent hole 4b communicating with the spiral groove 20 is formed in the eccentric part 4a, the refrigerant gas leaked from the compression chamber 10 into the roller part 8a and the refrigerant gas generated in the spiral groove 20 are a common gas. The oil can be easily discharged through the discharge hole 4c, and oil can be reliably supplied to the bearing sliding portion with a simple configuration.
[0034]
Also, a gas vent hole 4b extending radially outward from the gas discharge hole 4c and communicating with the eccentric portion 4a in the roller portion 8a, a gap between the main bearing 2 and the sub bearing 3, and a gas discharge hole 4c radially outward. Since the gas vent hole 4b that extends in the direction and communicates with the spiral groove 20 is formed independently, the refrigerant gas on the inner surface of the roller portion 8a interferes with the refrigerant gas foamed from the lubricating oil in the spiral groove 20. It can be extracted to the gas discharge hole 4c without any problem.
[0035]
As described above, by adopting the configuration of the present embodiment, the discharge passage 4b for discharging the refrigerant gas leaked from the compression chamber 10 into the roller portion 8a into the sealed container 6 with the suction pressure in the sealed container 6 is set. 4c and the spiral groove 20 for lubricating the bearing sliding portion can be separated, and the refrigerant gas and the lubricating oil do not interfere with each other, so that reliable lubrication to each sliding portion is possible, and high performance and reliability are achieved. A highly oscillating piston compressor can be provided.
[0036]
Next, a second embodiment of the present invention will be described with reference to FIGS. FIG. 6 is a longitudinal sectional view of a main part of a horizontally mounted oscillating piston compressor according to a second embodiment of the present invention, and FIG. 7 is a view in the direction of arrow C of the drive shaft portion of FIG.
[0037]
In this embodiment, the refrigerant gas discharge passage is the same as that described in the first embodiment, but the oil supply passage is mainly different. The oil supply mechanism of this embodiment will be described below.
[0038]
The lubricating oil 16 supplied through the oil supply pipe 19 by the same pump action described in the first embodiment flows into the hole 4d formed in the inside of the drive shaft 4 (the central portion of one side end), From this hole 4d, it passes through an oil outflow hole 4e formed so as to extend outward in the radial direction of the drive shaft 4, and is guided to a groove 4f formed on the auxiliary bearing 3 side, and further formed on the main bearing 2 side. By passing through the spiral groove 20, the auxiliary bearing 3, the eccentric portion 4a, and the main bearing 2 are lubricated. Here, since the centrifugal force due to the rotation of the drive shaft 4 is applied to the lubricating oil 16 passing through the oil outflow hole 4e, the amount of oil supply increases, and the lubricating oil can be stably supplied to each sliding portion.
[0039]
With the above configuration, the inside of the sealed container is set to the suction pressure, and the discharge passages 4b and 4c for discharging the refrigerant gas leaked from the compression chamber into the roller portion 8a into the sealed container and the bearing sliding portion are lubricated. Therefore, the refrigerant gas and the lubricating oil do not interfere with each other, and when the lubricating oil 16 passes through the oil outflow hole 4e, a centrifugal force due to the rotation of the drive shaft 4 is given. The amount of lubrication increases, reliable lubrication to each sliding portion is possible, and a high-performance and highly reliable oscillating piston compressor can be provided.
[0040]
Next, a third embodiment of the present invention will be described with reference to FIGS. 8 is a longitudinal sectional view of a vertically oscillating piston type compressor according to a third embodiment of the present invention, FIG. 9 is a sectional view taken along the line DD of FIG. 8, and FIG. It is.
[0041]
The compression operation of the vertically oscillating piston compressor of the present embodiment is the same as that of the horizontally oscillating piston compressor of the first embodiment, but the lubricating oil 16 stored in the lower part of the sealed container 6 is driven. The oil supply structure until pumping up to the shaft 4 is mainly different.
[0042]
The oil supply piece 4 g attached to the lower end of the drive shaft 4 is immersed in the lubricating oil 16 in the sealed container 6. As is apparent from FIG. 10, the lubrication oil 16 stored at the bottom of the sealed container 6 has a smaller diameter than the hole 4 d of the drive shaft 4 due to the centrifugal pump action caused by the rotation of the drive shaft 4. It is sucked from the oil supply piece 4g having an opening and supplied to the oil outflow hole 4e and the spiral groove 20 formed in the drive shaft 4, and the sliding portions are lubricated.
[0043]
Further, the refrigerant gas foamed from the lubricating oil 16 passing through the spiral groove 20 and the high-pressure refrigerant gas leaked from the compression chamber 10 into the roller portion 8a are formed inside the drive shaft 4 through the gas vent hole 4b. It reaches the gas discharge hole 4c and is discharged from the end of the drive shaft 4 into the sealed container 6 through the gas discharge hole 4c.
[0044]
In the case of a vertically installed compressor, the supply direction of the lubricating oil 16 to each sliding portion is opposite to the gravity, so that the amount of oil supply is insufficient and lubrication is likely to be poor. Since the centrifugal force due to the rotation of the drive shaft 4 is applied when the oil passage 16 passes through the oil outflow hole 4e, the amount of oil supply increases, and further, the viscous pump action of the spiral groove 20 supplies the auxiliary bearing 3, the eccentric portion 4a, and the main bearing 2. Therefore, even in the case of a vertical compressor, the lubricating oil 16 can be stably supplied to each sliding portion.
[0045]
Next, a fourth embodiment of the present invention will be described with reference to FIGS. FIG. 11 is a longitudinal sectional view of a horizontal type two-cylinder rotary compressor according to a fourth embodiment of the present invention, and FIG. 12 is an enlarged view of a main part of the compressor of FIG.
[0046]
In this embodiment, the cylinders 22a and 22b are respectively formed with cylindrical inner peripheral surfaces 22c and 22d at the center, and the main bearing 24 and the auxiliary bearing 25 are sandwiched by the partition plate 23 with the openings at both ends in the middle. Blocked. The partition plate 23, the main bearing 24, and the sub bearing 25 constitute end plates for the cylinders 22a and 22b. And the bearing parts 24a and 25a are formed in the center at the main bearing 24 and the sub bearing 25, respectively, and the drive shaft 26 is supported rotatably. The main bearing 24 and the sub-bearing 25 are fixed to the cylinders 22a and 22b, respectively, so that the rotation shaft of the drive shaft 26 coincides with the central axes of the cylindrical inner peripheral surfaces 22c and 22d of the cylinders 22a and 22b. Yes. An electric element rotor 5 is fixed to the drive shaft 26. The outer peripheral portion of the main bearing 24 is fixed to the sealed container 6, and the stator 7 of the electric element is fixed to the sealed container 6.
[0047]
The drive shaft 26 is formed with eccentric portions 26a and 26b at portions corresponding to the cylindrical inner peripheral surfaces 22c and 22d of the cylinders 22a and 22b. The cylindrical inner peripheral surfaces of the rollers 27a and 27b are rotatably fitted on the cylindrical outer peripheral surfaces of the eccentric portions 26a and 26b. The dimensions of each part are determined so that the gaps between the cylindrical outer peripheral surfaces of the rollers 27a and 27b and the cylindrical inner peripheral surfaces 22c and 22d of the cylinders 22a and 22b are very small. Further, vanes 28a and 28b are pressed against the cylindrical outer peripheral surfaces of the rollers 27a and 27b by springs 29a and 29b. Vane slots (not shown) are formed outside the cylindrical inner peripheral surfaces 22c and 22d of the cylinders 22a and 22b, and the vanes 28a and 28b are inserted into the vane slots. As a result, the vanes 28a and 28b move forward and backward in the vane slots toward the central axes of the cylindrical inner peripheral surfaces 22c and 22d of the cylinders 22a and 22b.
[0048]
With the above configuration, when the drive shaft 26 is rotated by the electric element, the rollers 27a and 27b revolve together with the eccentric portions 26a and 26b. By this revolving motion, the refrigerant gas is sucked into the sealed container 6 from the suction pipe 12 attached to the sealed container 6, passes through the suction passage 13, and then sucked into the cylinders 22a and 22b, thereby reducing the volume of the compression chamber. At the same time, the refrigerant gas sucked into the cylinder 22a is discharged from the discharge port 30a formed in the main bearing 24 into the discharge chamber 32a formed by the main bearing 24 and the discharge cover 31a, and then into the cylinder 22b. The sucked refrigerant gas is discharged from a discharge port 30b formed in the sub bearing 25 into a discharge chamber 32b formed by the sub bearing 25 and the discharge cover 31b. Thereafter, the refrigerant gas discharged into both discharge chambers 32a and 32b merges and is discharged from the discharge pipe 15 attached to the sealed container 6 to the outside of the compressor.
[0049]
In the case of the rotary compressor in which the inside of the hermetic container 6 is at the suction pressure in this embodiment, the back pressure for pressing the vanes 28a and 28b against the rollers 27a and 27b as in the case where the inside of the hermetic container 6 is high is eliminated. It is necessary to reinforce the force that presses the vane against the rollers, such as increasing the spring force of the springs 29a and 29b.
[0050]
The oil supply mechanism of the compression mechanism part of the present embodiment will be described. 11 and 12, the rotation of the drive shaft 26 causes the vane 28b to move forward and backward in a vane slot (not shown), and the volume of the space 22e in which the spring 29b is mounted changes. The lubricating oil 16 stored at the bottom of the sealed container 6 is sucked from the fluid diode 33 and pumped up to the drive shaft 26 through the oil supply pipe 19 by the pump action due to the volume change, and is provided on the outer periphery of the drive shaft 26. The main bearing 24, the auxiliary bearing 25, and the eccentric portions 26a and 26b are lubricated through the spiral groove 20 and returned to the sealed container again. A part of the lubricating oil 16 that lubricates the eccentric portions 26a and 26b is supplied to the suction chamber in the same manner as the oil pocket method described in the first embodiment. Here, even if the oil pocket is provided on any of the end surface of the main bearing 24, the end surface of the auxiliary bearing 25, and the end surface of the partition plate 23, the same action can be obtained.
[0051]
The refrigerant gas foamed from the lubricating oil 16 passing through the spiral groove 20 and the high-pressure refrigerant gas leaked from the compression chamber to the inner surfaces of the rollers 27a and 27b were formed inside the drive shaft 26 through the gas vent holes 34a and 34b. The gas is discharged into the sealed container 6 through the gas discharge hole 4c. Here, in the rollers 27a and 27b, the refrigerant gas leaking from the compression chamber 10 and the lubricating oil 16 that lubricates the eccentric portions 26a and 26b coexist, and the lubricating oil and the refrigerant are generated by the centrifugal force generated by the rotation of the drive shaft 26. Due to the difference in gas density, the high-density lubricating oil is located outside and the low-density refrigerant gas is located inside, so that only the refrigerant gas is formed inside the drive shaft 26 through the vent holes 34a and 34b. The gas can be discharged from the gas discharge hole 4c. In this case, the internal leakage can be suppressed without obstructing the oil supply by the oil pocket to the suction chamber necessary for the internal seal.
[0052]
With the above configuration, the spiral for lubricating the discharge passages 34a, 34b, 4c for discharging the refrigerant gas leaked into the rollers 27a, 27b from the compression chamber into the sealed container 6 and the sliding portions such as the bearings. Since the groove 20 can be separated and the refrigerant gas and the lubricating oil do not interfere with each other, reliable oil supply to each sliding portion is possible, and a high-performance and highly reliable rotary compressor can be provided.
[0053]
Next, a fifth embodiment of the present invention will be described with reference to FIGS. FIG. 13 is a longitudinal sectional view of a horizontal type oscillating piston type two-stage compressor according to a fifth embodiment of the present invention, and FIG. 14 is an enlarged view of a main part of the compressor of FIG.
[0054]
In this embodiment, the compression element 35 includes a low pressure compression element 35a and a high pressure compression element 35b. Openings at both ends of the cylinders 1 ′ and 1 ″ of the compression elements 35 a and 35 b are closed by a main bearing 24 that also serves as a shaft support for the drive shaft 26, a sub-bearing 25, and a partition plate 23. The auxiliary bearing 25 and the partition plate 23 constitute end plates for the cylinders 1 ′ and 1 ″. The compression operation of the oscillating piston compressor of this embodiment is basically the same as that of the oscillating piston compressor described in the first embodiment, but the flow of refrigerant gas is mainly different.
[0055]
The refrigerant gas enters the cylinder 1 ′ of the low-pressure compression element 35a through the suction pipe 36 attached to the sealed container 6 and is compressed. The compressed refrigerant gas passes through the discharge port 30 a formed in the main bearing 24, passes through the discharge silencer 41, and is discharged into the sealed container 6. The refrigerant gas discharged into the hermetic container 6 is discharged from the discharge pipe 37 to the outside and is radiated and cooled by the intermediate cooler 38, and then passes through the suction pipe 39 into the cylinder 1 "of the high pressure compression element 35b. The compressed refrigerant gas enters the discharge chamber 32b through the discharge port 30b provided in the sub-bearing 25, and flows out of the compressor through the discharge pipe 40 from here.
[0056]
The oil supply mechanism of the compression mechanism part of the present embodiment will be described. 13 and 14, the rotation of the drive shaft 26 causes the vane portion 8b "of the high pressure compression element 35b to move forward and backward in the hole portion 1c, and the volume of the hole portion 1c changes. The pump action due to this volume change. The lubricating oil 16 stored at the bottom of the sealed container 6 is sucked from the fluid diode 33, pumped up to the drive shaft 26 through the oil supply pipe 19, and passes through the spiral groove 20 provided on the outer periphery of the drive shaft 26. Then, the auxiliary bearing 25, the eccentric parts 26a and 26b, and the main bearing 24 are lubricated and returned to the sealed container 6. A part of the lubricating oil 16 that lubricated the eccentric part 26a of the compression element 35a for low pressure is part of the roller part 8a '. A part of the lubricating oil 16 supplied to the suction chamber by the pressure difference between the inside and the suction chamber and lubricated the eccentric portion 26b of the high pressure compression element 35b is the same as the oil pocket method described in the first embodiment. Provided to the suction chamber Here, even if the oil pocket is provided on either the end face of the auxiliary bearing 25 or the end face of the partition plate 23, the same action can be obtained.
[0057]
Refrigerant gas foamed from the lubricating oil 16 passing through the spiral groove 20 is guided to the gas discharge hole 4c formed in the drive shaft 26 through the gas vent holes 34a and 34b, and is transferred from the compression chamber of the high pressure compression element 35b to the roller. After the high-pressure refrigerant gas leaking into the portion 8a ″ is led to the gas discharge hole 4c through the gas vent hole 34b, these refrigerants pass through the gas discharge hole 4c from one end of the drive shaft 26. It is discharged into the sealed container 6.
[0058]
Here, in the roller portion 8 a ″ of the high pressure compression element 35 b, the refrigerant gas leaking from the compression chamber 10 and the lubricating oil 16 that lubricates the eccentric portion 26 b coexist, and the centrifugal force due to the rotation of the drive shaft 26 is present. Due to the difference in density between the lubricating oil and the refrigerant gas, the high-density lubricating oil is located on the outside, and the low-density refrigerant gas is located on the inside. The gas can be discharged from the gas discharge hole 4c formed in the interior, so that the high-pressure refrigerant gas can be prevented from entering the bearing sliding portion. The oil supply by the oil pocket to the required suction chamber is not obstructed, and an appropriate supply of lubricating oil into the cylinder can be realized to suppress internal leakage.
[0059]
With the above configuration, the discharge passages 34b and 4c for discharging the refrigerant gas leaked from the compression chamber into the roller portion 8a "into the sealed container 6 and the spiral groove 20 for lubricating the bearing sliding portion are provided. Separation is possible, and refrigerant gas and lubricating oil do not interfere with each other, so that reliable lubrication to each sliding portion is possible, and a high-performance and highly reliable laterally oscillating piston type two-stage compressor is provided. be able to.
[0060]
Next, a sixth embodiment of the present invention will be described with reference to FIG. FIG. 15 is a configuration diagram of the refrigeration cycle of the refrigeration apparatus according to the sixth embodiment of the present invention. This refrigeration cycle is an example of a cycle dedicated to refrigeration (cooling).
[0061]
In FIG. 15, the refrigeration cycle is formed by connecting a hermetic rotary compressor 45, a condenser 42, an expansion valve 43 that constitutes a pressure reducing device, and an evaporator 44 by piping. The condenser fan 42 a is forcibly sent to the condenser 42, and the evaporator fan 44 a is forcibly sent to the evaporator 44.
[0062]
When the hermetic rotary compressor 45 is started, the high-temperature and high-pressure working gas compressed by the hermetic rotary compressor 45 flows into the condenser 42 from the discharge pipe 15 as indicated by solid arrows, and is condensed. The heat is dissipated and liquefied by the blower action of the evaporator fan 42a, is throttled by the expansion valve 43, adiabatically expands to a low temperature / low pressure, and is absorbed and gasified by the evaporator 44 by the blower action of the evaporator fan 44a. 12 and sucked into the hermetic rotary compressor 45. The hermetic rotary compressor 45 is intermittently operated based on the operation command and the operation state detection signal.
[0063]
Since the refrigeration apparatus includes the above-described hermetic rotary compressor 45 of the present invention, a refrigeration system having excellent energy efficiency can be obtained. In particular, since the hermetic rotary compressor 45 of the present invention makes the inside of the hermetic container below the discharge pressure, the amount of high-temperature and high-pressure refrigerant flowing into the evaporator during intermittent operation can be reduced, and intermittent energy loss can be reduced. .
[0064]
In addition, although demonstrated using the single stage compressor here, a two stage compressor can also be mounted and it can apply not only to a freezing apparatus but to an air conditioner.
[0065]
【The invention's effect】
As described above, according to the present invention, the inside of the sealed container But Pressure lower than discharge pressure Even , Occurs in the oil groove formed in the sliding part of the bearing Refrigerant gas Through the refrigerant gas discharge passage formed inside the drive shaft It is possible to provide a high-performance and highly reliable hermetic rotary compressor and refrigeration / air-conditioning device that can be discharged into a hermetic container and can reliably lubricate the bearing sliding portion.
[0066]
Further, according to the present invention, the inside of the sealed container But Pressure lower than discharge pressure Even , Refrigerant gas leaking from the compression chamber to the inner surface of the roller Go through the oil groove Without interfering with lubricant Through the refrigerant gas discharge passage formed inside the drive shaft Refrigerant gas generated in the oil groove formed in the bearing sliding part can be discharged into the sealed container. The refrigerant gas It is possible to provide a high-performance and highly reliable hermetic rotary compressor that can discharge easily by sharing a discharge path and can reliably supply oil to the bearing sliding portion with a simple configuration.
[0067]
Further, according to the present invention, the inside of the sealed container But Intermediate pressure between discharge pressure and suction pressure Even , Occurs in the oil groove formed in the sliding part of the bearing Refrigerant gas Through the refrigerant gas discharge passage formed inside the drive shaft It is possible to provide a hermetic rotary compressor capable of discharging into a hermetic container and capable of reliably supplying oil to the bearing sliding portion and capable of two-stage compression with high performance and reliability.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a horizontally mounted swing piston compressor according to a first embodiment of the present invention.
FIG. 2 is a cross-sectional view taken along the line AA of FIG.
FIG. 3 is an operation explanatory diagram of the compression element of FIG. 2;
FIG. 4 is an enlarged view of a main part of the compressor of FIG.
5 is a view in the direction of arrow B of the drive shaft portion of FIG. 4;
FIG. 6 is a longitudinal sectional view of a main part of a horizontally mounted oscillating piston compressor of a second embodiment of the present invention.
7 is a view in the direction of the arrow C of the drive shaft portion of FIG. 6;
FIG. 8 is a longitudinal sectional view of a vertically oscillating piston type compressor according to a third embodiment of the present invention.
9 is a cross-sectional view taken along the line DD of FIG.
FIG. 10 is an enlarged view of a main part of the compressor of FIG.
FIG. 11 is a longitudinal sectional view of a horizontal two-cylinder rotary compressor according to a fourth embodiment of the present invention.
12 is an enlarged view of a main part of the compressor of FIG.
FIG. 13 is a longitudinal sectional view of a horizontally mounted swing piston type two-stage compressor according to a fifth embodiment of the present invention.
14 is an enlarged view of a main part of the compressor of FIG.
FIG. 15 is a configuration diagram of a refrigeration cycle of a refrigeration apparatus according to a sixth embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Cylinder, 1 '... Cylinder, 1 "... Cylinder, 1a ... Cylindrical inner peripheral surface, 1b ... Cylindrical hole part, 1c ... Hole part, 2 ... Main bearing, 2a ... Bearing part, 3 ... Sub bearing, 3a ... Bearing part, 3b ... discharge port, 3c ... discharge chamber, 4 ... drive shaft, 4a ... eccentric part, 4b ... gas vent hole, 4c ... gas discharge hole, 4d ... hole, 4e ... oil outflow hole, 4f ... groove, 4g ... refueling piece, 5 ... rotor, 6 ... sealed container, 7 ... stator, 8 ... swinging piston, 8a ... roller part, 8a '... roller part, 8a "... roller part, 8b ... vane part, 8b' ... Vane portion, 8b "... vane portion, 9 ... sliding member, 10 ... compression chamber, 11 ... suction chamber, 12 ... suction pipe, 13 ... suction passage, 14 ... discharge cover, 15 ... discharge pipe, 16 ... lubricating oil, 17 ... Suction fluid diode, 18 ... Discharge fluid diode, 19 ... Fueling pipe, 20 ... Spiral groove, DESCRIPTION OF SYMBOLS 1 ... Oil pocket, 22a, 22b ... Cylinder, 22c, 22d ... Cylindrical inner peripheral surface, 22e ... Space, 23 ... Partition plate, 24 ... Main bearing, 24a ... Bearing part, 25 ... Sub bearing, 25a ... Bearing part, 26 ... Drive shaft, 26a, 26b ... Eccentric part, 27a, 27b ... Roller, 28a, 28b ... Vane, 29a, 29b ... Spring, 30a, 30b ... Discharge port, 31a, 31b ... Discharge cover, 32a, 32b ... Discharge chamber 33 ... Fluid diode, 34a, 34b ... Gas vent hole, 35 ... Compression element, 35a ... Compression element for low pressure, 35b ... Compression element for high pressure, 36 ... Suction pipe, 37 ... Discharge pipe, 38 ... Intermediate cooler, 39 DESCRIPTION OF SYMBOLS ... Suction pipe, 40 ... Discharge pipe, 41 ... Discharge silencer, 42 ... Condenser, 42a ... Condenser fan, 43 ... Expansion valve, 44 ... Evaporator, 44a ... Evaporator fan, 4 ... sealed type rotary compressor.

Claims

An electric element and a compression element connected to the electric element are provided in the sealed container,
A cylinder chamber is formed by closing both ends of the cylinder of the compression element with end plates,
The outer periphery of the drive shaft is pivotally supported by the main bearing and the sub-bearing that the end plate has,
The roller is fitted an eccentric portion formed on the drive shaft inside and disposed in the cylinder chamber,
The refrigerant gas is compressed by revolving the roller in the cylinder chamber by the rotation of the drive shaft,
Hermetic rotary compressor for oil lubrication oil accumulated in the closed vessel bottom by oil pumping action by the rotation of the drive shaft, to the bearing sliding portion through the oil groove provided on the bearing sliding portion of the drive shaft In
The inside of the closed container is set to a pressure lower than the discharge pressure of the compression element,
With one end to form a refrigerant gas discharge passage and the other end is communicated is closed in said closed container inside of the drive shaft,
A hermetic rotary compressor characterized in that a refrigerant gas communication path extending radially outward from the refrigerant gas discharge path and communicating with a gap in the roller is formed in the eccentric portion.

2. The hermetic rotary compressor according to claim 1, wherein the refrigerant gas communication path is formed to communicate with a gap between both side surfaces of the eccentric portion and the end plates on both sides thereof. Hermetic rotary compressor.

2. The hermetic rotary compressor according to claim 1, wherein the refrigerant gas communication path is formed between the eccentric portion and the end plate formed outside a thrust bearing formed on one side of the eccentric portion. A hermetic rotary compressor formed so as to communicate with a gap.

An electric element and a compression element connected to the electric element are provided in the sealed container,
A cylinder chamber is formed by closing both ends of the cylinder of the compression element with end plates,
The outer periphery of the drive shaft is pivotally supported by the main bearing and the sub-bearing that the end plate has,
The roller is fitted an eccentric portion formed on the drive shaft inside and disposed in the cylinder chamber,
The refrigerant gas is compressed by revolving the roller in the cylinder chamber by the rotation of the drive shaft,
Tightly closed rotating the lubricating oil accumulated in the closed vessel bottom by oil pumping action by the rotation of the drive shaft, you refueling to the bearing sliding portion through the oil groove provided on the bearing sliding portion of the drive shaft In the compressor,
The inside of the closed container is set to a pressure lower than the discharge pressure of the compression element,
With one end to form a refrigerant gas discharge passage and the other end is communicated is closed in said closed container inside of the drive shaft,
Extending radially outward from the refrigerant gas discharge path to communicate with the gap between the eccentric portion in the roller and the end plate and extending radially outward from the refrigerant gas discharge path to the oil supply groove A hermetic rotary compressor characterized in that a communicating refrigerant gas communication passage is formed in the eccentric portion.

5. The hermetic rotary compressor according to claim 4, wherein the refrigerant gas communication path extends radially outward from the refrigerant gas discharge path and is a gap between the eccentric portion in the roller and the end plate. A hermetic rotary compressor characterized in that a communication passage communicating with the refrigerant gas and a communication passage extending radially outward from the refrigerant gas discharge passage and communicating with the oil supply groove are formed independently.

An electric element and a compression element connected to the electric element are provided in the sealed container,
This compression element is composed of two compression elements, a compression element for low pressure and a compression element for high pressure,
Both end openings of the cylinders of the compression elements are closed with end plates to form cylinder chambers of the compression elements,
The outer periphery of the drive shaft is pivotally supported by the main bearing and the sub-bearing that the end plate has,
A roller the eccentric portion is fitted to the inside of the respective compression element formed on the drive shaft arranged in the cylinder chamber of each compression element,
While revolving the roller in the cylinder chamber by the rotation of the drive shaft, the refrigerant gas is compressed in two stages,
Hermetic rotary compressor for oil lubrication oil accumulated in the closed vessel bottom by oil pumping action by the rotation of the drive shaft, to the bearing sliding portion through the oil groove provided on the bearing sliding portion of the drive shaft In
The inside of the closed container is an intermediate pressure between the discharge pressure and the suction pressure of the compression element,
With one end to form a refrigerant gas discharge passage and the other end is communicated is closed in said closed container inside of the drive shaft,
A refrigerant gas communication path extending radially outward from the refrigerant gas discharge path and communicating with a gap in the roller of the high pressure compression element is formed in an eccentric portion of the high pressure compression element. Hermetic rotary compressor.

A refrigerating cycle is configured by connecting a hermetic rotary compressor, a condenser, a decompression device, and an evaporator with piping,
The hermetic rotary compressor includes an electric element and a compression element connected to the electric element in the hermetic container, and operates intermittently, and the inside of the hermetic container is set to a pressure lower than the discharge pressure of the compression element,
The compression element is
A cylinder chamber is formed by closing both ends of the cylinder with end plates.
The outer periphery of the drive shaft is pivotally supported by the main bearing and the sub-bearing that the end plate has,
The roller is fitted an eccentric portion formed on the drive shaft inside and disposed in the cylinder chamber,
The refrigerant gas is compressed by revolving the roller in the cylinder chamber by the rotation of the drive shaft,
Wherein the closed vessel bottom accumulated lubricating oil, and the oil supply to the bearing sliding portion through the oil groove provided on the bearing sliding portion of the drive shaft by oil pumping action by the rotation of the drive shaft,
With one end to form a refrigerant gas discharge passage and the other end is communicated is closed in said closed container inside of the drive shaft,
A refrigeration / air-conditioning apparatus, wherein a refrigerant gas communication path extending radially outward from the refrigerant gas discharge path and communicating with a gap in the roller is formed in the eccentric portion.