JP3560901B2 - Scroll compressor - Google Patents

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Publication number
JP3560901B2
JP3560901B2 JP2000180279A JP2000180279A JP3560901B2 JP 3560901 B2 JP3560901 B2 JP 3560901B2 JP 2000180279 A JP2000180279 A JP 2000180279A JP 2000180279 A JP2000180279 A JP 2000180279A JP 3560901 B2 JP3560901 B2 JP 3560901B2
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Japan
Prior art keywords
scroll component
back pressure
component
orbiting scroll
scroll
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JP2000180279A
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Japanese (ja)
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JP2001355584A (en
Inventor
作田  淳
飯田  登
澤井  清
修一 山本
定幸 山田
敬 森本
博之 河野
博正 芦谷
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Panasonic Corp
Panasonic Holdings Corp
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Panasonic Corp
Matsushita Electric Industrial Co Ltd
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Description

【0001】
【発明の属する技術分野】
本発明は、主として冷凍空調機、冷凍機等に使用されるスクロール圧縮機に関するものである。
【0002】
【従来の技術】
冷凍空調機や冷凍機に用いられるスクロール圧縮機は、一般に、鏡板から渦巻ラップが立ち上がる固定スクロール部品および旋回スクロール部品を噛み合わせて双方間に圧縮室を形成し、旋回スクロール部品を自転拘束機構による自転の拘束のもとに円軌道に沿って旋回させたとき圧縮室が容積を変えながら移動することで吸入、圧縮、吐出を行い、旋回スクロール部品の外周部に所定の背圧を潤滑用のオイルにより印加し、旋回スクロール部品が固定スクロール部品から離れて転覆するようなことがないようにしている。
【0003】
しかし、運転中の固定スクロール部品と旋回スクロール部品は、前記背圧が中央部に印加するさらに高い背圧によって常に接触摺動しているため、その接触面で摩擦が生じ、これが摺動損失となって駆動力増大の原因となっている。これに対処するのに特公平01−34313号公報は、図4に示すようなスクロール圧縮機を提案している。
【0004】
このものは、固定スクロール部品101の旋回スクロールとの摺動面102を、固定スクロール部品101の外縁101aに沿ったリング状に形成して、背圧側から圧縮室の低圧側へのオイル、つまり背圧流体の漏れを防止するのに必要な旋回スクロール部品との接触によるシールを確保しながら、摺動面102の外まわりに設けた凹部103により摺動面102のリング形状を一定幅以下に抑えることにより摺動面102での旋回スクロールとの接触面積が小さくなって、摺動損失が低減するようにしている。
【0005】
また凹部103は旋回スクロール部品の外周部まわりのオイルで充満した空間を旋回スクロールの摺動面に対向して形成し、ここに運転中の旋回スクロール部品の外周部が出入りしてオイルがよく付着し摺動面102との摺動部に多くのオイルを持ち込めるようにするので、摺動面102に十分な給油が行える。また、凹部103による前記環状空間の広がりで旋回スクロール部品がその外周に溜まったオイルを攪拌するのを緩和するので、オイル攪拌による損失を低減することができる。
【0006】
【発明が解決しようとする課題】
しかし、上記従来の技術では、固定スクロール部品101に設ける摺動面102は、固定スクロール部品101の円形な縁101aに沿った円形のリング状とされているため、少なくとも固定スクロール部品101における巻き終わり1周分を円形状としなければならず、その結果圧縮室が吸入を行う吸入室の容積が増えて吸入過熱の原因となり、冷凍能力が低下するといった問題が生じる。また、凹部103は固定スクロール部品101における渦巻ラップ104の巻き終わり径と縁101aとの間に一定の幅でしか設けられないので、固定スクロール部品101を大型化しないで凹部103を設けようとすると余り大きくできず、旋回スクロールによる環状空間でのオイルの攪拌を抑制し駆動力を軽減する効果は余り得られない。
【0007】
本発明の目的は、吸入室の増大とそれによる吸入過熱の問題なく、また、摺動損失や背圧流体の攪拌による駆動力の増大を抑えて、背圧側と圧縮室の低圧側との間のシールが確保できるスクロール圧縮機を提供することにある。
【0008】
【課題を解決するための手段】
上記の目的を達成するために、本発明のスクロール圧縮機は、鏡板から渦巻ラップが立ち上がる固定スクロール部品および旋回スクロール部品を噛み合わせて双方間に圧縮室を形成し、旋回スクロール部品を自転拘束機構による自転の拘束のもとに円軌道に沿って旋回させたとき圧縮室が容積を変えながら移動することで吸入、圧縮、吐出を行い、旋回スクロール部品の外周部に所定の背圧を印加したものにおいて、固定スクロール部品の鏡板における渦巻ラップ外まわりにある、旋回スクロールの鏡板との対向面に、前記固定スクロール部品の渦巻ラップと一体に形成され、渦巻ラップの最外周の内壁面から外方へ前記内壁面にほぼ沿った外壁面を持つように広がり旋回スクロールの鏡板と摺接する環状のシール部と、このシール部の外側に位置する環状の凹部とを形成したことを主たる特徴としている。
【0009】
このような構成では、旋回スクロール部品は自転拘束機構により自転を拘束されて円軌道に沿って旋回駆動されながら外周部への背圧の印加によって固定スクロール部品から浮いて転覆するようなことなく、それらの鏡板から立ち上がり噛み合っている渦巻ラップ間の圧縮室により吸入、圧縮、吐出を行い、同時に、固定スクロール部品における鏡板の渦巻ラップの外まわりにある環状のシール部が、旋回スクロールの鏡板に摺接して固定スクロール部品における渦巻ラップ形成領域を連続に囲って前記背圧側と圧縮室の低圧側とを仕切るので、背圧流体が圧縮室の低圧側に不用意に漏れるのを防止して前記背圧を保証し、圧縮機能を安定させる。
【0010】
特に、環状のシール部は固定スクロール部品の渦巻ラップと一体で、その内壁面から外方へ広がったもので、渦巻ラップとの間に遊びがない上その厚さを前記シールに活かして前記内壁面にほぼ沿った非円形な外壁面を持つように形成するので、前記シール確保のために圧縮室が吸入を行う部分の容積が従来のように大きくなることはなく吸入過熱による能力低下の問題が解消する。また、シール部は渦巻ラップ最外周部との協働によりシール確保のために単独の厚さをもつ必要がなく前記外方への広がりは少なくてよいので、旋回スクロールとの摺動面積が小さくなって摺動損失が従来のものよりも低減するし、シール部の外側にある凹部は通常の渦巻ラップの最外周部近くから固定スクロール部品の取り付け部などを持った外周部近くまで広く設けることができ、これにより、旋回スクロール部品の外周まわりの背圧のための環状空間を平面的に大きくして旋回スクロール部品が背圧流体を攪拌するのを十分に抑制し、前記摺動損失の低減と相まって駆動力を従来のものよりも低減することができる。
【0011】
前記シール部の幅は前記固定スクロール部品の渦巻ラップの厚さの半分以上大きくしたものとすると、シール部の幅を可能な限り小さく抑えて摺動摩擦による摺動損失を極力低減しながら、必要なシールを確実に満足することができる。
【0012】
前記凹部の深さは、前記固定スクロール部品のラップ溝深さをHmmとしたとき、0.1mm以上H/5mm以下に設定するのが好適であり、0.1mm以上にて旋回スクロール部品の摺動面において、背圧流体によって生じる粘性損失を防ぐことができ、H/5mm以下に抑えて強度や加工性の低下の問題を回避することができる。
【0013】
前記凹部の外周は、前記旋回スクロール部品の旋回径よりも外側とするのが好適であり、固定スクロール部品と旋回スクロール部品との摺動部に噛み込んだ異物が凹部を通って環状空間に排出されるので、摺動部の密着性が高まり、背圧側から圧縮室の低圧側に背圧流体が不用意に漏れるのを防止することができる。
【0014】
固定スクロール部品に設けられた背圧側と圧縮室の低圧側とを繋ぐ連通路の途中に背圧側が所定の圧力を越えたとき前記低圧側に逃がす背圧調整機構を有し、前記連通路が前記凹部にて背圧側に開口していると、連通路は背圧側に対して凹部を介し常時通じるので、背圧調整機構による背圧の調整が中断しないし、背圧流体は所定より高圧となる都度圧縮室の低圧側に逃がされるので、背圧流体がオイルであると圧縮室まわりの摺動部の潤滑とシールに役立ち、圧縮機の性能が向上しかつ安定する。
【0015】
本発明のそれ以上の目的および特徴は、以下の詳細な説明および図面の記載によって明らかになる。本発明の各特徴は、可能な限りにおいてそれ単独で、あるいは種々な組み合わせで複合して用いることができる。
【0016】
【発明の実施の形態】
以下、本発明の実施の形態に係るスクロール圧縮機につき、図1〜図3を参照して詳細に説明し、本発明の理解に供する。
【0017】
本実施の形態のスクロール圧縮機は図1〜図3に符号31を付して示してある。このスクロール圧縮機31は図1、図2に示すように、鏡板21、22から渦巻ラップ21a、22aが立ち上がる固定スクロール部品2および旋回スクロール部品4を噛み合わせて双方間に圧縮室5を形成し、旋回スクロール部品4を図3に示す自転拘束機構24による自転の拘束のもとに円軌道に沿って旋回させたとき圧縮室5が容積を変えながら移動することで吸入、圧縮、吐出を行う。このとき、旋回スクロール部品4はその背面、特に外周部に所定の背圧が印加されて、固定スクロール部品2から離れて転覆するようなことなく、前記吸入、圧縮、吐出を安定に行う。
【0018】
圧縮室5は図示の場合、複数形成され固定、旋回各スクロール部品2、4の外周側から中央に移動しながら容積が小さくなり、固定スクロール部品2の外周部に設けられている図3に示す吸入口3から冷媒を吸入して中央に移動しながら次第に圧縮し、固定スクロール部品2の中央部に設けられた吐出口6を通じて吐出する。
【0019】
吐出口6にはリード弁28が設けられ、圧縮される冷媒が所定の圧力以上になる都度開いて吐出させることにより冷媒の吐出圧を保証している。
【0020】
背圧は、冷凍空調機や冷凍機にスクロール圧縮機31を用いる場合の一例として、旋回スクロール部品4の中央部背面に設けた背圧室29に供給する潤滑用のオイルの供給圧によって印加するようにしている。しかし、本発明はこれに限られることはない。スクロール圧縮機31の用途や動作形式などの違いによって他の背圧流体を用いることができる。
【0021】
上記背圧を保証するため、図1、図2に示すように、固定スクロール部品2における鏡板21の渦巻ラップ21a外まわりにある、旋回スクロール部品4の鏡板22との対向面12に、渦巻ラップ21aの最外周の内壁面21bから外方へ渦巻ラップ21aの前記内壁面21bにほぼ沿った外壁面21cを持つように広がり旋回スクロール部品4の鏡板22と摺接する環状のシール部13と、このシール部13の外側に位置する環状の凹部14とを形成してある。
【0022】
このようにすると、スクロール圧縮機31が前記吸入、圧縮、吐出を行うのに伴い、環状のシール部13は図1に示すように固定スクロール部品2の渦巻ラップ21aと、特に最外周部分と一体で、その内壁面21bの最外周の図1に符号15a〜15dを付して示す一周分の内壁面から外方へ広がったもので、渦巻ラップ21aとの間に遊びがない上その厚さを前記シールに活かして前記内壁面15a〜15dにほぼ沿った非円形な外壁面21cを持つように形成するので、前記シール確保のために圧縮室5が吸入を行う部分の容積、例えば図1、図2に示す吸入室の容積が従来のように大きくなることはなく吸入過熱による能力低下の問題が解消する。
【0023】
また、シール部13は渦巻ラップ21aの最外周部との協働によりシール確保のために単独の厚さを持つ必要がなく前記外方への広がり量は少なくてよいので、旋回スクロール部品4との摺動面積が従来のものよりも小さくなって摺動損失が従来のものよりも低減するし、シール部13の外側にある凹部14は通常の渦巻ラップ21aの最外周部近くから固定スクロール部品2の取り付け部などを持った外周部2c近くまで広く設けることができ、これにより、旋回スクロール部品4の外周まわりの背圧のための環状空間8を平面的に大きくして旋回スクロール部品4が背圧流体を攪拌するのを十分に抑制し、前記摺動損失の低減と相まって駆動力を従来のものよりも低減することができる。
【0024】
前記シール部13の幅13tは前記固定スクロール部品2の渦巻ラップ21aの厚さtの半分以上大きくしたものとすると、つまり、13t=t/2以上に設定すると、シール部13の幅を可能な限り小さく抑えて摺動摩擦による摺動損失を極力低減しながら、必要なシールを確実に満足することができる。
【0025】
前記凹部14の深さ14hは、前記固定スクロール部品2のラップ溝深さ12hをHmmとしたとき、0.1mm以上H/5mm以下とするのが好適である。0.1mm以上とすることにより旋回スクロール部品4の摺動面4a1において、背圧流体であるオイルなどによって生じる粘性損失を防ぐことができ、H/5mm以下とすることにより強度や彫り込みの加工性が低下するのを回避することができる。
【0026】
前記凹部14の外周14aは、図1に示すように前記旋回スクロール部品4の旋回径4aよりも外側とすると、固定スクロール部品2のシール部13と旋回スクロール部品4の摺動面4aとの摺動部の間に噛み込んだ異物が凹部14を通って環状空間8に排出されるので、前記摺動面の密着性が高まり、前記背圧側から圧縮室5の低圧側に背圧流体であるオイルなどが不用意に漏れるのを防止することができる。
【0027】
固定スクロール部品2に設けられた前記背圧側と圧縮室5の低圧側との間を繋ぐ連絡路10の途中に、背圧側が所定の中間圧を越えたときに前記低圧側に逃がす背圧調整機構9を有し、連通路10は前記凹部14にて背圧側に開口している。16はその開口を示す。これにより、連絡路10は背圧側に対して凹部14を介し常時通じるので、背圧調整機構9による背圧の調整が中断しないし、背圧流体は所定より高圧になる都度圧縮室5の低圧側に逃がされるので、背圧流体がオイルであると圧縮室5まわりの摺動部の潤滑とシールに役立ち、スクロール圧縮機31の性能が向上しかつ安定する。
【0028】
本実施の形態の図示するスクロール圧縮機31はさらに、冷凍サイクル機器と接続されて密閉状態になる容器41内に設けたいわゆる密閉型スクロール圧縮機の場合の一例であり、主としてメンテナンスフリーな使用がなされる。また、縦向きに設置される場合を示しているが、横向きに設置される場合もある。
【0029】
スクロール圧縮機31は図3に示すように容器41内の上部に設けられ、駆動軸42の上向きな一端部を支持する主軸受部材7によって固定されている。主軸受部材7は容器41の内周に焼き嵌めや溶接によって取り付けられ、これに固定スクロール部品2がボルト止めなどして固定されている。旋回スクロール部品4は主軸受部材7と固定スクロール部品2との間に挟み込まれて固定スクロール部品2と噛み合い、相互間に圧縮室5を形成している。旋回スクロール部品4と主軸受部材7との間にオルダムリングが自転拘束機構24として設けられ、主軸受部材7との間で旋回スクロール部品4の自転を拘束する。しかし、自転拘束機構24は既に知られまた以降提供される他の形式の部材や機構を採用することができる。
【0030】
容器41内には電動機45も設けられ、スクロール圧縮機31を駆動するようにしている。電動機45は容器41の内周に焼き嵌めや溶接などして固定された固定子45aと、固定子45aの内側に位置する回転子45bとを備え、回転子45bは駆動軸42に固定されている。駆動軸42はその固定子45aを固定した部分の下方に伸びた他端を容器41の内周に溶接などして固定された副軸受部材46により軸受されている。
【0031】
駆動軸42の上向きの一端にある偏心したクランク軸42aが旋回スクロール部品4の背面にある前記背圧室29を持った旋回孔47に嵌り合っている。これらにより、駆動軸42が電動機45により駆動されると、自転拘束機構24と協働して、旋回スクロール部品4を所定の円軌道に沿って旋回させる。
【0032】
駆動軸42の下向きの他端にはポンプ147が設けられ、スクロール圧縮機31と同時に駆動される。これによりポンプ147は容器41の底部に設けられたオイル溜まり48にあるオイル49を吸い上げて駆動軸42内を通縦している通路51を通じて背圧室29に供給する。このときの供給圧は、スクロール圧縮機31の吐出圧とほぼ同等であり、旋回スクロール部品4の外周に対する背圧源ともする。これにより、旋回スクロール部品4は前記圧縮によっても固定スクロール部品2から離れたり転覆したりするようなことはなく、所定の圧縮機能を安定して発揮する。
【0033】
背圧室29に供給されたオイル49の一部は、前記供給圧や自重によって、逃げ場を求めるようにしてクランク軸42aと旋回スクロール部品4の旋回孔47との嵌り合い部、駆動軸42と主軸受部材7との間の軸受部53に進入してそれぞれの部分を潤滑した後落下し、オイル溜まり48へ戻る。背圧室29に供給されたオイル49の別の一部は通路54を通って固定スクロール部品2と旋回スクロール部品4との噛み合せによる摺動部と、旋回スクロール部品4の外周部まわりにあって自転拘束機構24が位置している環状空間8とに分岐して進入し、前記噛み合せによる摺動部および自転拘束機構24の摺動部を潤滑するのに併せ、環状空間8にて旋回スクロール部品4の背圧を印加する。
【0034】
前記環状空間8に進入するオイルは絞り57での絞り作用によって前記背圧と圧縮室5の低圧側との圧力の中間となる中圧に設定される。環状空間8は背圧室29の高圧側との間がシール58によってシールされていて、進入してくるオイルが充満するにつれて圧力を増し所定の圧力を越えると、背圧調整機構9の弁11が開いて圧縮室5の低圧側に戻され進入する。このオイルの進入は所定の周期で繰り返され、この繰り返しのタイミングは前記吸収、圧縮、吐出の繰り返しサイクル、絞り57による減圧設定と背圧調整機構9での圧力設定との関係、の組み合わせによって決まり、固定スクロール部品2と旋回スクロール部品4との噛み合せによる摺動部への意図的な潤滑となる。この意図的な潤滑は前記したように連絡路10の凹部14への開口(16)によって常時保証される。吸入室26へと供給されたオイル49は旋回スクロール部品4の旋回運動とともに圧縮室5へと移動し、圧縮室5間の漏れ防止に役立っている。
【0035】
スクロール圧縮機31から吐出される冷媒はスクロール圧縮機31上にボルト止めなどされたマフラー62内に入って後、通路63を通じてスクロール圧縮機31の下に回り、電動機45の回転子45b部を通って旋回しながら電動機45の下に至り、オイル49を遠心分離して振り落としオイル溜まり48に戻す。オイル49を分離した冷媒は電動機45の固定子45aを通って電動機45上に達した後、図示しない通路を通じてスクロール圧縮機31のマフラー62上に至り吐出パイプ163から容器41外に吐出され冷凍サイクルに供給される。冷凍サイクルを経た冷媒は容器41の吸入パイプ1に戻り吸入口3から圧縮室5に吸入され、以降同じ動作を繰り返す。
【0036】
【発明の効果】
本発明によれば、上記の記載から明らかなように、旋回スクロールの外周部に所定の背圧を与えながら吸入、圧縮、吐出を行うのに、固定スクロールに環状に設けられる旋回スクロールとの間のシール部が、固定スクロール部品の渦巻ラップと一体で、その内壁面から外方へ広がったもので、渦巻ラップとの間に遊びがない上その厚さを前記シールに活かして前記内壁面にほぼ沿った非円形な外壁面を持つように形成するので、前記シール確保のために圧縮室が吸入を行う部分の容積が従来のように大きくなることはなく吸入過熱による能力低下の問題が解消する。また、シール部は渦巻ラップ最外周部との協働によりシール確保のために単独の厚さをもつ必要がなく前記外方への広がりは少なくてよいので、旋回スクロールとの摺動面積が小さくなって摺動損失が従来のものよりも低減するし、シール部の外側にある凹部は通常の渦巻ラップの最外周部近くから固定スクロール部品の取り付け部などを持った外周部近くまで広く設けることができ、これにより、旋回スクロール部品の外周まわりの背圧のための環状空間を平面的に大きくして旋回スクロール部品が背圧流体を攪拌するのを十分に抑制し、前記摺動損失の低減と相まって駆動力を従来のものよりも低減することができる。
【0037】
前記シール部の幅は前記固定スクロール部品の渦巻ラップの厚さの半分以上大きくしたものとすることで、シール部の幅を可能な限り小さく抑えて摺動摩擦による摺動損失を極力低減しながら、必要なシールを確実に満足することができる。
【0038】
前記凹部の深さは、前記固定スクロール部品のラップ溝深さをHmmとしたとき、0.1mm以上H/5mm以下に設定することで、0.1mm以上にて旋回スクロール部品の摺動面において背圧流体によって生じる粘性損失を防ぐことができ、H/5mm以下に抑えて強度や加工性の低下の問題を回避することができる。
【0039】
前記凹部の外周は、前記旋回スクロール部品の旋回径よりも外側とすることにより、固定スクロール部品と旋回スクロール部品との摺動部に噛み込んだ異物が凹部を通って環状空間に排出されるので、摺動部の密着性が高まり、背圧側から圧縮室の低圧側に背圧流体が不用意に漏れるのを防止することができる。
【0040】
固定スクロール部品に設けられた背圧側と圧縮室の低圧側とを繋ぐ連通路の途中に背圧側が所定の圧力を越えたとき前記低圧側に逃がす背圧調整機構を有し、前記連通路は前記凹部にて背圧側に開口したものとすることにより、連通路が背圧側に対して凹部を介し常時通じるので、背圧調整機構による背圧の調整が中断しないし、背圧流体は所定より高圧となる都度圧縮室の低圧側に逃がされるので、背圧流体がオイルであると圧縮室まわりの摺動部の潤滑とシールに役立ち、圧縮機の性能が向上しかつ安定する。
【図面の簡単な説明】
【図1】本発明の1つの実施の形態を示すスクロール圧縮機の要部である固定スクロール部品の平面図である。
【図2】図1の固定スクロール部品を持ったスクロール圧縮機の要部の断面図である。
【図3】図2のスクロール圧縮機の全体構成を示す断面図である。
【図4】従来のスクロール圧縮機の固定スクロールを示す平面図である。
【符号の説明】
2 固定スクロール部品
3 吸入口
4 旋回スクロール部品
5 圧縮室
6 吐出口
8 環状空間
9 背圧調整機構
10 連絡路
11 弁
12 対向面
12h ラップ溝深さ
13 シール部
13t シール部厚さ
14 凹部
14a 凹部外周
14h 凹部深さ
15a〜15d 最外周内壁面
16 開口
21、22 鏡板
21a、22a 渦巻ラップ
21b 内壁面
21c 外壁面
[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a scroll compressor mainly used for a refrigerating air conditioner, a refrigerating machine, and the like.
[0002]
[Prior art]
In general, scroll compressors used in refrigerating air conditioners and refrigerators form a compression chamber between the fixed scroll component and the orbiting scroll component in which the spiral wrap rises from the end plate, and the orbiting scroll component is rotated by a rotation restricting mechanism. When swiveling along a circular orbit under the constraint of rotation, the compression chamber moves while changing its volume to perform suction, compression and discharge, and a predetermined back pressure is applied to the outer periphery of the orbiting scroll part for lubrication. The oil is applied to prevent the orbiting scroll component from overturning away from the fixed scroll component.
[0003]
However, since the fixed scroll component and the orbiting scroll component are constantly in contact and sliding due to the higher back pressure applied to the central portion during operation, friction occurs at the contact surface, and this causes sliding loss. This causes the driving force to increase. To cope with this, Japanese Patent Publication No. 01-34313 proposes a scroll compressor as shown in FIG.
[0004]
In this device, the sliding surface 102 of the fixed scroll component 101 with the orbiting scroll is formed in a ring shape along the outer edge 101a of the fixed scroll component 101, and the oil from the back pressure side to the low pressure side of the compression chamber, The ring shape of the sliding surface 102 is suppressed to a certain width or less by the concave portion 103 provided around the outer surface of the sliding surface 102 while securing the seal by the contact with the orbiting scroll component necessary for preventing the leakage of the pressurized fluid. Accordingly, the contact area of the sliding surface 102 with the orbiting scroll is reduced, and the sliding loss is reduced.
[0005]
The recess 103 forms a space filled with oil around the outer periphery of the orbiting scroll component, facing the sliding surface of the orbiting scroll. The outer periphery of the orbiting scroll component during operation enters and exits, and the oil adheres well. Since a large amount of oil can be brought into the sliding portion with the sliding surface 102, sufficient oil can be supplied to the sliding surface 102. Further, since the orbiting scroll component agitates the oil accumulated on the outer periphery thereof due to the expansion of the annular space formed by the concave portion 103, the loss due to the oil agitation can be reduced.
[0006]
[Problems to be solved by the invention]
However, in the above-described conventional technique, the sliding surface 102 provided on the fixed scroll component 101 is formed in a circular ring shape along the circular edge 101a of the fixed scroll component 101. One round must be circular, and as a result, the volume of the suction chamber in which the compression chamber suctions increases, causing suction overheating and causing a problem that the refrigerating capacity decreases. Further, since the concave portion 103 is provided only with a fixed width between the winding end diameter of the spiral wrap 104 and the edge 101a in the fixed scroll component 101, if the concave portion 103 is provided without increasing the size of the fixed scroll component 101. It cannot be too large, and the effect of suppressing the stirring of oil in the annular space by the orbiting scroll and reducing the driving force cannot be obtained much.
[0007]
An object of the present invention is to eliminate the problem of increase in the suction chamber and the resulting overheating of the suction chamber, and to suppress the increase in the driving force due to the sliding loss and the agitation of the back-pressure fluid, so that the space between the back-pressure side and the low-pressure side of the compression chamber is reduced An object of the present invention is to provide a scroll compressor capable of securing a seal.
[0008]
[Means for Solving the Problems]
In order to achieve the above object, a scroll compressor according to the present invention includes a fixed scroll component and a orbiting scroll component in which a spiral wrap rises from a head plate, and a compression chamber is formed between the fixed scroll component and the orbiting scroll component. When swiveling along a circular orbit under the constraint of rotation, the suction chamber performs suction, compression, and discharge by moving while changing the volume, and applied a predetermined back pressure to the outer peripheral portion of the orbiting scroll component. In the above , the outer surface of the spiral wrap of the end plate of the fixed scroll component is formed integrally with the spiral wrap of the fixed scroll component on the surface facing the end plate of the orbiting scroll, and extends outward from the outermost inner wall surface of the spiral wrap. An annular seal portion that extends so as to have an outer wall surface substantially along the inner wall surface and is in sliding contact with the end plate of the orbiting scroll; It is mainly characterized in that to form an annular recess located.
[0009]
In such a configuration, the orbiting scroll component is restrained from rotating by the rotation restricting mechanism and is not driven to float from the fixed scroll component by the application of the back pressure to the outer peripheral portion while being orbitally driven along the circular orbit, and to overturn. The suction, compression, and discharge are performed by the compression chambers between the spiral wraps that rise and mesh with the end plates, and at the same time, the annular seal portion around the end of the end plate spiral wrap in the fixed scroll component slides on the end plate of the orbiting scroll. As a result, the back pressure side and the low pressure side of the compression chamber are continuously surrounded by surrounding the spiral wrap forming area of the fixed scroll component, so that the back pressure fluid is prevented from inadvertently leaking to the low pressure side of the compression chamber, and Guarantee and stabilize the compression function.
[0010]
In particular, the annular seal portion is integral with the spiral wrap of the fixed scroll component and extends outward from the inner wall surface. There is no play between the spiral wrap and the spiral wrap, and the inner thickness is utilized for the seal by utilizing its thickness. Since it is formed so as to have a non-circular outer wall surface substantially along the wall surface, the volume of the portion where the suction is performed by the compression chamber for securing the seal does not increase as in the conventional case, and there is a problem that the capacity is reduced due to suction overheating. Is eliminated. Further, the seal portion does not need to have a single thickness for securing the seal in cooperation with the outermost peripheral portion of the spiral wrap, and the outward spread may be small, so that the sliding area with the orbiting scroll is small. As a result, the sliding loss is reduced as compared with the conventional one, and the concave part outside the seal part should be provided widely from near the outermost part of the normal spiral wrap to near the outer part with the fixed scroll part mounting part etc. Thereby, the annular space for the back pressure around the outer periphery of the orbiting scroll component is enlarged in a plane to sufficiently suppress the orbiting scroll component from agitating the back pressure fluid, thereby reducing the sliding loss. Thus, the driving force can be reduced as compared with the conventional one.
[0011]
Assuming that the width of the seal portion is set to be at least half the thickness of the spiral wrap of the fixed scroll component, it is necessary to keep the width of the seal portion as small as possible and reduce sliding loss due to sliding friction as much as possible. The seal can be surely satisfied.
[0012]
When the depth of the wrap groove of the fixed scroll component is H mm, the depth of the concave portion is preferably set to 0.1 mm or more and H / 5 mm or less. On the moving surface, it is possible to prevent the viscous loss caused by the back pressure fluid, and to suppress the viscosity to H / 5 mm or less, thereby avoiding the problem of deterioration in strength and workability.
[0013]
It is preferable that the outer periphery of the concave portion is outside the orbital diameter of the orbiting scroll component, and foreign matter caught in the sliding portion between the fixed scroll component and the orbiting scroll component is discharged to the annular space through the concave portion. Therefore, the adhesion of the sliding portion is enhanced, and it is possible to prevent the back pressure fluid from inadvertently leaking from the back pressure side to the low pressure side of the compression chamber.
[0014]
In the middle of a communication path connecting the back pressure side provided in the fixed scroll component and the low pressure side of the compression chamber, a back pressure adjusting mechanism that releases to the low pressure side when the back pressure side exceeds a predetermined pressure, wherein the communication path is If the recess is open to the back pressure side, the communication path is always open to the back pressure side via the recess, so that the back pressure adjustment by the back pressure adjustment mechanism is not interrupted, and the back pressure fluid has a pressure higher than a predetermined value. Since the fluid is released to the low pressure side of the compression chamber each time, if the back pressure fluid is oil, it helps lubrication and sealing of sliding parts around the compression chamber, and the performance of the compressor is improved and stabilized.
[0015]
Further objects and features of the present invention will become apparent from the following detailed description and drawings. Each feature of the present invention can be used alone or in combination in various combinations as far as possible.
[0016]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, a scroll compressor according to an embodiment of the present invention will be described in detail with reference to FIGS. 1 to 3 to provide an understanding of the present invention.
[0017]
The scroll compressor according to the present embodiment is shown in FIGS. As shown in FIGS. 1 and 2, the scroll compressor 31 meshes the fixed scroll component 2 and the orbiting scroll component 4 in which the spiral wraps 21a and 22a rise from the end plates 21 and 22 to form a compression chamber 5 therebetween. When the orbiting scroll component 4 is turned along a circular orbit under the constraint of rotation by the rotation restricting mechanism 24 shown in FIG. 3, the compression chamber 5 moves while changing its volume to perform suction, compression and discharge. . At this time, a predetermined back pressure is applied to the back surface, particularly the outer peripheral portion, of the orbiting scroll component 4, and the orbiting scroll component 4 stably performs the suction, compression, and discharge without falling away from the fixed scroll component 2.
[0018]
In the illustrated case, a plurality of compression chambers 5 are formed, and the volume thereof decreases while moving from the outer peripheral side of each of the fixed and orbiting scroll components 2 and 4 to the center, and is provided on the outer peripheral portion of the fixed scroll component 2 as shown in FIG. The refrigerant is sucked from the suction port 3, gradually compressed while moving to the center, and discharged through the discharge port 6 provided at the center of the fixed scroll component 2.
[0019]
The discharge port 6 is provided with a reed valve 28, which opens and discharges the refrigerant to be compressed each time the pressure becomes equal to or higher than a predetermined pressure, thereby ensuring the discharge pressure of the refrigerant.
[0020]
The back pressure is applied by a supply pressure of lubricating oil to be supplied to a back pressure chamber 29 provided at the center rear surface of the orbiting scroll component 4 as an example in a case where the scroll compressor 31 is used for a refrigerating air conditioner or a refrigerator. Like that. However, the present invention is not limited to this. Other back-pressure fluids can be used depending on the application of the scroll compressor 31 and the type of operation.
[0021]
As shown in FIGS. 1 and 2, in order to guarantee the back pressure, the spiral wrap 21a is provided on the surface 12 of the fixed scroll component 2 facing the end plate 22 of the orbiting scroll component 4 around the outer periphery of the spiral wrap 21a. An annular seal portion 13 that extends outward from an outermost inner wall surface 21b of the spiral wrap 21a so as to have an outer wall surface 21c substantially along the inner wall surface 21b of the spiral wrap 21a, and is in sliding contact with the end plate 22 of the orbiting scroll component 4. An annular concave portion 14 located outside the portion 13 is formed.
[0022]
In this manner, as the scroll compressor 31 performs the suction, compression, and discharge, the annular seal portion 13 is integrated with the spiral wrap 21a of the fixed scroll component 2 as shown in FIG. The outer peripheral surface of the inner wall surface 21b extends outward from the inner wall surface for one round, which is denoted by reference numerals 15a to 15d in FIG. 1, and has no play between the spiral wrap 21a and its thickness. Is formed to have a non-circular outer wall surface 21c substantially along the inner wall surfaces 15a to 15d by utilizing the seal, so that the volume of a portion where the compression chamber 5 performs suction, for example, FIG. In addition, the capacity of the suction chamber shown in FIG. 2 does not increase as in the conventional case, and the problem of the capacity reduction due to the overheating of the suction is solved.
[0023]
In addition, the seal portion 13 does not need to have a single thickness for securing the seal in cooperation with the outermost peripheral portion of the spiral wrap 21a, and the amount of outward spread may be small. The sliding area is smaller than that of the conventional one, the sliding loss is smaller than that of the conventional one, and the concave portion 14 outside the seal portion 13 is fixed near the outermost periphery of the normal spiral wrap 21a. 2 can be provided as wide as the vicinity of the outer peripheral portion 2c having the mounting portion, etc., whereby the annular space 8 for the back pressure around the outer periphery of the orbiting scroll component 4 is enlarged in a plane, and Agitation of the back pressure fluid can be sufficiently suppressed, and the driving force can be reduced as compared with the conventional one, in combination with the reduction of the sliding loss.
[0024]
When the width 13t of the seal portion 13 is set to be at least half the thickness t of the spiral wrap 21a of the fixed scroll component 2, that is, when 13t = t / 2 or more, the width of the seal portion 13 becomes possible. The required seal can be surely satisfied while keeping the sliding loss as small as possible while minimizing the sliding loss.
[0025]
The depth 14h of the recess 14 is preferably not less than 0.1 mm and not more than H / 5 mm when the wrap groove depth 12h of the fixed scroll component 2 is Hmm. By setting the thickness to 0.1 mm or more, it is possible to prevent a viscous loss caused by oil or the like as a back pressure fluid on the sliding surface 4a1 of the orbiting scroll component 4. Can be prevented from decreasing.
[0026]
As shown in FIG. 1, when the outer periphery 14a of the concave portion 14 is outside the orbital diameter 4a of the orbiting scroll component 4, sliding between the seal portion 13 of the fixed scroll component 2 and the sliding surface 4a of the orbiting scroll component 4 is performed. Since the foreign matter caught between the moving parts is discharged to the annular space 8 through the concave portion 14, the adhesion of the sliding surface is enhanced, and the back pressure fluid flows from the back pressure side to the low pressure side of the compression chamber 5. Inadvertent leakage of oil and the like can be prevented.
[0027]
In the middle of a communication path 10 connecting the back pressure side provided on the fixed scroll component 2 and the low pressure side of the compression chamber 5, a back pressure adjustment to be released to the low pressure side when the back pressure side exceeds a predetermined intermediate pressure. It has a mechanism 9, and the communication passage 10 is open to the back pressure side in the recess 14. Reference numeral 16 denotes the opening. As a result, the communication path 10 always communicates with the back pressure side via the concave portion 14, so that the back pressure adjustment by the back pressure adjusting mechanism 9 is not interrupted, and the back pressure fluid becomes low pressure in the compression chamber 5 every time the pressure becomes higher than a predetermined value. When the back pressure fluid is oil, it is useful for lubrication and sealing of the sliding portion around the compression chamber 5, and the performance of the scroll compressor 31 is improved and stabilized.
[0028]
The illustrated scroll compressor 31 of the present embodiment is an example of a so-called hermetic scroll compressor provided in a container 41 which is connected to a refrigeration cycle device and is in a hermetically sealed state, and is mainly used for maintenance-free use. Done. In addition, although the case where it is installed vertically is shown, it may be installed horizontally.
[0029]
As shown in FIG. 3, the scroll compressor 31 is provided at an upper portion in the container 41, and is fixed by the main bearing member 7 that supports one upward end of the drive shaft 42. The main bearing member 7 is attached to the inner periphery of the container 41 by shrink fitting or welding, and the fixed scroll component 2 is fixed thereto by bolting or the like. The orbiting scroll component 4 is sandwiched between the main bearing member 7 and the fixed scroll component 2 and meshes with the fixed scroll component 2 to form a compression chamber 5 therebetween. An Oldham ring is provided as a rotation restricting mechanism 24 between the orbiting scroll component 4 and the main bearing member 7, and restricts the rotation of the orbiting scroll component 4 between the orbiting scroll component 4 and the main bearing member 7. However, the rotation restraining mechanism 24 can employ other types of members and mechanisms that are already known and provided later.
[0030]
An electric motor 45 is also provided in the container 41 to drive the scroll compressor 31. The electric motor 45 includes a stator 45a fixed to the inner periphery of the container 41 by shrink fitting or welding, and a rotor 45b positioned inside the stator 45a. The rotor 45b is fixed to the drive shaft 42. I have. The drive shaft 42 is supported by a sub-bearing member 46 having the other end extending below the portion to which the stator 45 a is fixed, fixed to the inner periphery of the container 41 by welding or the like.
[0031]
An eccentric crankshaft 42a at the upper end of the drive shaft 42 fits into the orbiting hole 47 having the back pressure chamber 29 on the back of the orbiting scroll component 4. Thus, when the drive shaft 42 is driven by the electric motor 45, the orbiting scroll component 4 is turned along a predetermined circular orbit in cooperation with the rotation restricting mechanism 24.
[0032]
A pump 147 is provided at the other lower end of the drive shaft 42 and is driven at the same time as the scroll compressor 31. As a result, the pump 147 sucks up the oil 49 in the oil sump 48 provided at the bottom of the container 41 and supplies the oil 49 to the back pressure chamber 29 through the passage 51 passing through the drive shaft 42. The supply pressure at this time is substantially equal to the discharge pressure of the scroll compressor 31, and also serves as a back pressure source for the outer periphery of the orbiting scroll component 4. Accordingly, the orbiting scroll component 4 does not separate from or overturns the fixed scroll component 2 even by the compression, and exhibits a predetermined compression function stably.
[0033]
A part of the oil 49 supplied to the back pressure chamber 29 is provided with the drive shaft 42 and the fitting portion between the crankshaft 42a and the orbiting hole 47 of the orbiting scroll component 4 so that a relief area is obtained by the supply pressure and the own weight. After entering the bearing 53 between the main bearing member 7 and lubricating each part, it falls and returns to the oil sump 48. Another part of the oil 49 supplied to the back pressure chamber 29 passes through the passage 54 and is located around the sliding portion formed by the engagement between the fixed scroll component 2 and the orbiting scroll component 4 and around the outer peripheral portion of the orbiting scroll component 4. In addition to branching into and entering the annular space 8 in which the rotation restraining mechanism 24 is located, and lubricating the sliding portion of the engagement and the sliding portion of the rotation restraining mechanism 24, the orbiting scroll component is formed in the annular space 8. A back pressure of 4 is applied.
[0034]
The oil entering the annular space 8 is set to a medium pressure which is intermediate between the back pressure and the pressure on the low pressure side of the compression chamber 5 by the throttle action of the throttle 57. The annular space 8 is sealed by a seal 58 between the high pressure side of the back pressure chamber 29 and the pressure increases as the inflowing oil fills and exceeds a predetermined pressure. Opens and returns to the low pressure side of the compression chamber 5 and enters. The entry of the oil is repeated at a predetermined cycle, and the timing of this repetition is determined by a combination of the above-described cycle of the absorption, compression, and discharge, and the relationship between the pressure reduction setting by the throttle 57 and the pressure setting by the back pressure adjusting mechanism 9. In addition, the fixed scroll component 2 and the orbiting scroll component 4 are engaged with each other, so that the sliding portion is intentionally lubricated. This intentional lubrication is always ensured by the opening (16) into the recess 14 of the communication channel 10 as described above. The oil 49 supplied to the suction chamber 26 moves to the compression chamber 5 together with the orbiting movement of the orbiting scroll component 4, which helps prevent leakage between the compression chambers 5.
[0035]
Refrigerant discharged from the scroll compressor 31 enters a muffler 62 bolted to the scroll compressor 31, and then goes under the scroll compressor 31 through a passage 63 and passes through a rotor 45 b of the electric motor 45. The oil 49 is centrifuged down and shaken down to return to the oil sump 48 while turning. The refrigerant from which the oil 49 has been separated passes through the stator 45 a of the electric motor 45, reaches the electric motor 45, reaches the muffler 62 of the scroll compressor 31 through a passage (not shown), is discharged from the discharge pipe 163 to the outside of the container 41, and is subjected to the refrigeration cycle. Supplied to The refrigerant that has passed through the refrigeration cycle returns to the suction pipe 1 of the container 41, is drawn into the compression chamber 5 from the suction port 3, and thereafter repeats the same operation.
[0036]
【The invention's effect】
According to the present invention, as is apparent from the above description, suction, compression, and discharge are performed while applying a predetermined back pressure to the outer peripheral portion of the orbiting scroll. The seal portion is integral with the spiral wrap of the fixed scroll component and extends outward from the inner wall surface, there is no play between the spiral wrap and the thickness of the spiral wall wrap is utilized on the inner wall surface by utilizing the thickness for the seal. Since it is formed so as to have a substantially non-circular outer wall surface, the volume of the portion where the compression chamber suctions for securing the seal does not become large as in the conventional case, and the problem of capacity reduction due to suction overheating is solved. I do. Further, the seal portion does not need to have a single thickness to secure the seal in cooperation with the outermost peripheral portion of the spiral wrap, and the outward spread may be small, so that the sliding area with the orbiting scroll is small. As a result, the sliding loss is reduced as compared with the conventional one, and the concave part outside the seal part should be provided widely from near the outermost part of the normal spiral wrap to near the outer part with the fixed scroll part mounting part etc. Thereby, the annular space for the back pressure around the outer periphery of the orbiting scroll component is enlarged in a plane to sufficiently suppress the orbiting scroll component from agitating the back pressure fluid, thereby reducing the sliding loss. Thus, the driving force can be reduced as compared with the conventional one.
[0037]
By making the width of the seal portion at least half the thickness of the spiral wrap of the fixed scroll component, while keeping the width of the seal portion as small as possible and reducing the sliding loss due to sliding friction as much as possible, The required seal can be satisfied with certainty.
[0038]
When the depth of the concave portion is set to 0.1 mm or more and H / 5 mm or less when the depth of the wrap groove of the fixed scroll component is Hmm, the depth of the concave portion is 0.1 mm or more on the sliding surface of the orbiting scroll component. Viscous loss caused by back-pressure fluid can be prevented, and the problem of deterioration in strength and workability can be avoided by suppressing the viscosity to H / 5 mm or less.
[0039]
By setting the outer periphery of the concave portion outside the orbital diameter of the orbiting scroll component, the foreign matter caught in the sliding portion between the fixed scroll component and the orbiting scroll component is discharged to the annular space through the concave portion. In addition, the adhesion of the sliding portion is enhanced, and it is possible to prevent the back pressure fluid from inadvertently leaking from the back pressure side to the low pressure side of the compression chamber.
[0040]
In the middle of a communication path connecting the back pressure side provided on the fixed scroll component and the low pressure side of the compression chamber, a back pressure adjusting mechanism that releases to the low pressure side when the back pressure side exceeds a predetermined pressure, wherein the communication path is Since the communication path is always open to the back pressure side through the recess by being opened to the back pressure side in the recess, the back pressure adjustment by the back pressure adjustment mechanism is not interrupted, and the back pressure fluid is higher than a predetermined value. Each time the pressure becomes high, the oil is released to the low pressure side of the compression chamber. Therefore, if the back pressure fluid is oil, it is useful for lubrication and sealing of the sliding portion around the compression chamber, and the performance of the compressor is improved and stabilized.
[Brief description of the drawings]
FIG. 1 is a plan view of a fixed scroll component which is a main part of a scroll compressor according to an embodiment of the present invention.
FIG. 2 is a sectional view of a main part of a scroll compressor having the fixed scroll component of FIG.
FIG. 3 is a cross-sectional view showing the overall configuration of the scroll compressor of FIG.
FIG. 4 is a plan view showing a fixed scroll of a conventional scroll compressor.
[Explanation of symbols]
2 Fixed scroll part 3 Inlet 4 Orbiting scroll part 5 Compression chamber 6 Discharge port 8 Annular space 9 Back pressure adjusting mechanism 10 Communication path 11 Valve 12 Opposing surface 12h Lapping groove depth 13 Seal part 13t Seal part thickness 14 Recess 14a Recess Outer circumference 14h Depth of recess 15a to 15d Outermost inner wall 16 Openings 21, 22 End plates 21a, 22a Spiral wrap 21b Inner wall 21c Outer wall

Claims (5)

鏡板から渦巻ラップが立ち上がる固定スクロール部品および旋回スクロール部品を噛み合わせて双方間に圧縮室を形成し、旋回スクロール部品を自転拘束機構による自転の拘束のもとに円軌道に沿って旋回させたとき圧縮室が容積を変えながら移動することで吸入、圧縮、吐出を行い、旋回スクロール部品の外周部に所定の背圧を印加するようにしたスクロール圧縮機において、固定スクロール部品の鏡板における渦巻ラップ外まわりにある、旋回スクロールの鏡板との対向面に、前記固定スクロール部品の渦巻ラップと一体に形成され、渦巻ラップの最外周の内壁面から外方へ前記内壁面にほぼ沿った外壁面を持つように広がり旋回スクロールの鏡板と摺接する環状のシール部と、このシール部の外側に位置する環状の凹部とを形成したことを特徴とするスクロール圧縮機。When the fixed scroll component and the orbiting scroll component, in which the spiral wrap rises from the end plate, are engaged with each other to form a compression chamber, and the orbiting scroll component is turned along a circular orbit under the constraint of rotation by the rotation constraint mechanism. In a scroll compressor that performs suction, compression, and discharge by moving the compression chamber while changing the volume, and applies a predetermined back pressure to the outer periphery of the orbiting scroll component, the outer periphery of the spiral wrap around the end plate of the fixed scroll component The orbiting scroll has an outer wall surface formed integrally with the spiral wrap of the fixed scroll component on the surface facing the end plate of the orbiting scroll, and extending outwardly from the innermost wall surface of the spiral scroll wrap and substantially along the inner wall surface. An annular seal portion which extends in sliding contact with the end plate of the orbiting scroll, and an annular recess located outside the seal portion. Scroll compressor according to claim. 前記シール部の幅は前記固定スクロール部品の渦巻ラップの厚さの半分以上大きくした請求項1に記載のスクロール圧縮機。The scroll compressor according to claim 1, wherein a width of the seal portion is larger than a half of a thickness of a spiral wrap of the fixed scroll component. 前記凹部の深さは、前記固定スクロール部品のラップ溝深さをHmmとしたとき、0.1mm以上H/5mm以下とした請求項1、2のいずれか1項に記載のスクロール圧縮機。3. The scroll compressor according to claim 1, wherein a depth of the concave portion is 0.1 mm or more and H / 5 mm or less when a wrap groove depth of the fixed scroll component is H mm. 4. 前記凹部の外周は、前記旋回スクロール部品の旋回径よりも外側とした請求項1〜3のいずれか1項に記載のスクロール圧縮機。The scroll compressor according to any one of claims 1 to 3, wherein an outer periphery of the concave portion is outside a turning diameter of the orbiting scroll component. 固定スクロール部品に設けられた背圧側と圧縮室の低圧側とを繋ぐ連通路の途中に背圧側が所定の圧力を越えたときに前記低圧側に逃がす背圧調整機構を有し、連通路は前記凹部にて背圧側に通じている請求項1〜4のいずれか1項に記載のスクロール圧縮機。In the middle of a communication path connecting the back pressure side provided in the fixed scroll component and the low pressure side of the compression chamber, a back pressure adjustment mechanism is provided that releases to the low pressure side when the back pressure side exceeds a predetermined pressure. The scroll compressor according to any one of claims 1 to 4, wherein the scroll communicates with the back pressure side at the concave portion.
JP2000180279A 2000-06-15 2000-06-15 Scroll compressor Expired - Lifetime JP3560901B2 (en)

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CN100396930C (en) * 2003-10-17 2008-06-25 松下电器产业株式会社 Scroll compressor
US7229261B2 (en) 2003-10-17 2007-06-12 Matsushita Electric Industrial Co., Ltd. Scroll compressor having an annular recess located outside an annular seal portion and another recess communicating with suction port of fixed scroll
JP2008202560A (en) * 2007-02-22 2008-09-04 Sanden Corp Scroll type fluid machine
TW201120316A (en) 2009-12-04 2011-06-16 Ind Tech Res Inst Self-sealing scroll compressor
CN102094824B (en) * 2009-12-11 2013-03-13 财团法人工业技术研究院 Self-sealing mechanism of scroll compressor
JP5440202B2 (en) * 2010-01-21 2014-03-12 パナソニック株式会社 Manufacturing method of scroll compressor

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