JPH05187369A - Scroll compressor - Google Patents
Scroll compressorInfo
- Publication number
- JPH05187369A JPH05187369A JP17518792A JP17518792A JPH05187369A JP H05187369 A JPH05187369 A JP H05187369A JP 17518792 A JP17518792 A JP 17518792A JP 17518792 A JP17518792 A JP 17518792A JP H05187369 A JPH05187369 A JP H05187369A
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- back pressure
- pressure chamber
- scroll
- oil supply
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明はスクロール圧縮機に係
り、旋回スクロールへの背圧力制御に関するものであ
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor, and more particularly to a back pressure control for an orbiting scroll.
【０００２】[0002]
【従来の技術】近年、工作機械の発展に伴い実用化され
つつあり低振動、低騒音特性を備えた圧縮機として注目
を浴びているスクロール圧縮機は、例えば特開昭５９−
４９３８６号公報にも示されているように吸入室が外周
部にあり吐出ポートがうず巻きの中心部に設けられ、圧
縮流体の流れが一方向のため高速運転時の流体抵抗が小
さくて圧縮効率が高いことは一般によく知られている。
また、この種の高圧ガス密閉シェル構造の圧縮機は、特
開昭５９−４９３８６号公報で知られるように図５に示
す構成あるいは特開昭５５−１４８９９４号公報で知ら
れるように図６に示す構成、あるいは前記の特開昭５５
−１４８９９４号公報の圧縮機を上、下に転倒させた形
態の特開昭５７−６８５７９号公報の構成などが提案さ
れ、背圧室の適切な圧力設定により軸方向のスラスト力
を軽減しながら各摺動部の潤滑が次のように構成されて
いた。すなわち図５においては、固定スクロールラップ
１２３は駆動軸１０５を支承する本体フレーム１０２に
取付けられた鏡板１２１に固定され、旋回スクロールラ
ップ１１６はラップ支持円盤１１５に固定され、このラ
ップ支持円盤１１５は、鏡板１２１と本体フレーム１０
２との間に背圧室１２０に微少隙間を有した遊合状態で
配置され、自転阻止機能と背圧室の仕切り機能を備えた
オルダムリング１１８を介して旋回可能に支承され、さ
らに端部に駆動用のモータ１１０と偏心部をもつ駆動軸
１０５によって旋回運動をする。そして吸入・圧縮され
たガスは密閉シェル１０１内に吐出する。吐出ガスから
分離した潤滑油は密閉シェル１０１の底部の油溜に収集
され、駆動軸１０５の下端に開口して偏心状態で設けら
れた油穴１０６、および駆動軸１０５を支承する軸受の
微少隙間を通して漸次減圧しながら遠心ポンプ作用を利
用して高圧圧力状態で背圧室１２０に導かれる。さらに
オルダムリング１１８の摺動部の微少隙間を経て吐出圧
力と吸入圧力との中間圧力にまで減圧された潤滑油は、
鏡板１２１に設けた細穴のバランス通路１２６を通して
吸入室１２２に流入する過程で摺動部を潤滑する構成で
あった。また図６においては、背圧室２２０はオルダム
リング２１８によって圧力的に仕切られてもなく、吸入
室２２２との連通もないが旋回スクロールのラップ支持
円盤２１５に設けられた細穴のバランス通路２２６によ
って適当な位置の圧縮室２４０と連通されており、この
バランス通路２２６はラップ支持円盤２１５が旋回運動
することによって開閉されて背圧室２２０と圧縮室２４
０との間の間欠給油通路を構成しており、また、背圧室
２２０の摺動部や駆動軸２０５の各軸受部は吐出ガスで
充満された密閉シェル２０１の底部の油溜２０９とは駆
動軸２０５に設けられ油穴２０６と駆動軸２０５を支承
する軸受の微少隙間によって連通され遠心ポンプと差圧
によって給油される。2. Description of the Related Art In recent years, scroll compressors, which have been put into practical use with the development of machine tools and have been attracting attention as compressors having low vibration and low noise characteristics, have been disclosed in, for example, Japanese Patent Laid-Open No. 59-59.
As also disclosed in Japanese Patent No. 49386, the suction chamber is provided at the outer peripheral portion and the discharge port is provided at the center of the vortex winding, and since the flow of the compressed fluid is in one direction, the fluid resistance during high-speed operation is small and the compression efficiency is high. High is generally well known.
Further, a compressor having a high-pressure gas closed shell structure of this type has a structure shown in FIG. 5 as known from Japanese Patent Laid-Open No. 59-49386 or a structure shown in FIG. 6 as known from Japanese Laid-Open Patent No. 55-148994. The structure shown, or the above-mentioned JP-A-55
A configuration of JP-A-57-68579, in which the compressor of JP-A-148994 is turned upside down, is proposed, and the thrust force in the axial direction is reduced by appropriately setting the back pressure chamber. Lubrication of each sliding portion was configured as follows. That is, in FIG. 5, the fixed scroll wrap 123 is fixed to the end plate 121 attached to the main body frame 102 supporting the drive shaft 105, the orbiting scroll wrap 116 is fixed to the lap support disk 115, and the wrap support disk 115 is End plate 121 and body frame 10
It is arranged in a back pressure chamber 120 in a loose state with a small gap between the two, and is rotatably supported via an Oldham ring 118 having a rotation preventing function and a back pressure chamber partitioning function, and further, an end portion. Further, the motor 110 for driving and the drive shaft 105 having an eccentric portion make a turning motion. Then, the sucked and compressed gas is discharged into the closed shell 101. Lubricating oil separated from the discharge gas is collected in an oil sump at the bottom of the closed shell 101, is opened in the lower end of the drive shaft 105 and is provided in an eccentric oil hole 106, and a minute gap in the bearing that supports the drive shaft 105. While being gradually depressurized, the gas is introduced into the back pressure chamber 120 in a high pressure state by utilizing the centrifugal pump action. Further, the lubricating oil that has been reduced to an intermediate pressure between the discharge pressure and the suction pressure through the minute gap in the sliding portion of the Oldham ring 118 is
The sliding portion is lubricated in the process of flowing into the suction chamber 122 through the fine balance passage 126 provided in the end plate 121. Further, in FIG. 6, the back pressure chamber 220 is neither partitioned by pressure by the Oldham ring 218 nor communicated with the suction chamber 222, but a fine hole balance passage 226 provided in the lap support disk 215 of the orbiting scroll. Is communicated with the compression chamber 240 at an appropriate position by means of which the balance passage 226 is opened and closed by the lap support disk 215 making a pivotal movement, so that the back pressure chamber 220 and the compression chamber 24 are opened.
0 constitutes an intermittent oil supply passage, and the sliding portion of the back pressure chamber 220 and each bearing portion of the drive shaft 205 are different from the oil reservoir 209 at the bottom of the closed shell 201 filled with the discharge gas. The drive shaft 205 is communicated with an oil hole 206 and a minute gap of a bearing that supports the drive shaft 205, and is communicated with a centrifugal pump by differential pressure.
【０００３】[0003]
【発明が解決しようとする課題】しかしながら上記の図
５のような背圧室１２０内から吸入室１２２までの絞り
通路の開度が固定された給油通路の構成では、圧縮機運
転速度や高低圧側の負荷条件等により背圧室１２０から
吸入室１２２に流入する潤滑油の温度が異なり、それに
伴って潤滑油の粘性も変化し、背圧室１２０から吸入室
１２２へ潤滑油流入室が異なる。その結果、特定の運転
条件で背圧室１２０の圧力が適切設定されていても圧縮
機運転条件が異なる場合には、背圧室１２０の圧力が異
常上昇したり、異常低下する。そのことによって、旋回
スクロール１１４が固定スクロール１３４に過度に押圧
されたり、また旋回スクロール１１４が固定スクロール
１３４から離れたりして摺動部の異常摩耗や動力損失，
圧縮効率の異常低下を招くと共に、吸入室１２２に流入
する潤滑油量にも過不足が生じ、潤滑油流入過大による
圧縮効率の低下、潤滑油不足による圧縮室隙間の油膜シ
ール効果低下に起因する異常温度上昇を招くという問題
があった。また、図６の場合も背圧室２２０と圧縮室２
４０との間を連通するバランス通路２２６の開度が固定
しているため、上記と同様の問題があった。なお、背圧
室の圧力を異常上昇させない方策として、（１）特開昭
５７−７６２９１号公報、（２）特開昭５８−１６０５
８３号公報，特開昭５８−１７６４８９号公報，特開昭
５８−１８３８８７号公報、（３）特開昭５６−１６５
７８７号公報の構成が提案されている。すなわち、
（１）は、背圧室と吸入側とを制御弁を介して連通さ
せ、背圧室圧力が異常上昇した時、制御弁を開通させて
背圧室の流体を吸入側に流出させ、背圧室圧力を制御す
る構成である。また、（２）は、背圧室圧力が吐出圧力
よりも高くなった時、制御弁を開いて吸入側または吐出
ガス圧力側に連通させて背圧室圧力を制御する構成であ
る。また（３）は、吐出圧力側の油を背圧室に係わる摺
動面に差圧給油しながら、吐出ガスを減圧調整して背圧
室に導き、背圧室を中間圧力に維持する構成である。し
かしながら、（１）の構成では、背圧室へ流入したり、
背圧室から流出するガス流量のみを制御するので、背圧
室への油供給の配慮がされておらず、背圧室に係わる部
材の摩耗が著しいという問題があった。また、（２）の
構成では、背圧室圧力が吐出圧力よりも低く制御される
のみで、旋回スクロールを固定スクロール側に押圧し過
ぎ、その結果、旋回スクロールと固定スクロールとの間
の摺動面の摩耗が早く、摩擦損失が大きいという問題が
あった。また、（３）の構成では、背圧室への給油路と
ガス導入路とが別構成のため、油が背圧室全域に分散し
にくく、部分的に油不足が生じて焼付きが生じる。ま
た、粘性の小さい吐出ガスを減圧調整して背圧室圧力を
制御するので、減圧調整バラツキが大きく、背圧室の圧
力設定が困難であるという問題があった。また、（１）
〜（３）を組み合わせた構成、すなわち、吐出ガス圧力
の作用する油溜から適当な絞り給油通路を経て背圧室に
差圧給油し、背圧室と吸入室（または圧縮室）との間を
（１）のような制御弁を介して連通し、背圧室圧力が異
常上昇した時のみ制御弁を開通して背圧室圧力を正常圧
力に復帰させる構成が考えられるが、背圧室と吸入室
（または圧縮室）との間の開閉を繰り返すことによって
圧縮負荷や背圧室圧力が急激に変化し、負荷トルクの変
動，旋回スクロールのバタ付きに起因する異音発生，背
圧室から吸入室（または圧縮室）にガスが吹き抜ける際
に生じるガス吹き抜け音等によりスクロール圧縮機本来
の低振動・低騒音特性を損なうという重要な問題があっ
た。一方、背圧室の圧力を異常低下させない方策とし
て、特開昭５８−１６０５８０号公報の構成が提案され
ている。この構成は、背圧室と吐出ガス通路側とを連通
する通路を設け、背圧室圧力が設定圧力よりも低くなっ
た時、通路途中の制御弁を開通させて吐出ガス通路側か
ら高圧ガスを背圧室に流入させ、背圧室圧力が低くなり
過ぎないように制御する構成である。しかしながら、こ
の構成でも上記特開昭５７−７６２９１号公報の場合と
同様に、背圧室への給油量を常に確保する配慮がなされ
ておらず、上記同様の問題があった。そこで、本発明は
給油通路途中の背圧室と吸入室（または圧縮室）との間
の絞り通路の開度を連続的に変化させて背圧室圧力を制
御することにより低振動・低騒音特性・耐久性に優れた
スクロール圧縮機を提供するものである。However, in the configuration of the oil supply passage in which the opening of the throttle passage from the inside of the back pressure chamber 120 to the suction chamber 122 as shown in FIG. 5 is fixed, the compressor operating speed and the high and low pressure side are increased. The temperature of the lubricating oil flowing from the back pressure chamber 120 into the suction chamber 122 varies depending on the load conditions of the above, and the viscosity of the lubricating oil changes accordingly, and the lubricating oil inflow chamber from the back pressure chamber 120 to the suction chamber 122 varies. As a result, even if the pressure in the back pressure chamber 120 is appropriately set under a specific operating condition, if the compressor operating condition is different, the pressure in the back pressure chamber 120 abnormally rises or falls. As a result, the orbiting scroll 114 is excessively pressed by the fixed scroll 134, or the orbiting scroll 114 is separated from the fixed scroll 134, resulting in abnormal wear of the sliding portion and power loss.
This causes an abnormal decrease in compression efficiency and causes an excess or deficiency in the amount of lubricating oil flowing into the suction chamber 122, resulting in a decrease in compression efficiency due to excessive inflow of lubricating oil and a decrease in the oil film sealing effect in the compression chamber gap due to insufficient lubricating oil. There was a problem of causing an abnormal temperature rise. In the case of FIG. 6 also, the back pressure chamber 220 and the compression chamber 2
Since the opening degree of the balance passage 226 communicating with 40 is fixed, there is a problem similar to the above. As measures for preventing the pressure in the back pressure chamber from rising abnormally, (1) JP-A-57-76291 and (2) JP-A-58-1605.
83, JP-A-58-176489, JP-A-58-183887, (3) JP-A-56-165.
The configuration of Japanese Patent No. 787 has been proposed. That is,
In (1), the back pressure chamber and the suction side are communicated with each other via a control valve, and when the pressure in the back pressure chamber rises abnormally, the control valve is opened to allow the fluid in the back pressure chamber to flow out to the suction side. This is a configuration for controlling the pressure in the pressure chamber. Further, (2) has a configuration in which when the back pressure chamber pressure becomes higher than the discharge pressure, the control valve is opened to communicate with the suction side or the discharge gas pressure side to control the back pressure chamber pressure. Further, (3) is a configuration in which while the oil on the discharge pressure side is differentially supplied to the sliding surface related to the back pressure chamber, the discharge gas is decompressed and guided to the back pressure chamber to maintain the back pressure chamber at an intermediate pressure. Is. However, in the configuration of (1), it may flow into the back pressure chamber,
Since only the flow rate of gas flowing out from the back pressure chamber is controlled, no consideration has been given to the oil supply to the back pressure chamber, and there has been a problem that the wear of the members related to the back pressure chamber is remarkable. Further, in the configuration of (2), the back pressure chamber pressure is only controlled to be lower than the discharge pressure, and the orbiting scroll is pressed to the fixed scroll side too much, resulting in sliding between the orbiting scroll and the fixed scroll. There was a problem that the wear of the surface was fast and the friction loss was large. Further, in the configuration of (3), since the oil supply passage to the back pressure chamber and the gas introduction passage are separately configured, oil is difficult to disperse in the entire back pressure chamber, and oil shortage occurs partially and seizure occurs. .. Further, since the pressure of the back pressure chamber is controlled by adjusting the pressure of the discharge gas having a low viscosity, there is a large variation in the pressure reduction adjustment, which makes it difficult to set the pressure of the back pressure chamber. Also, (1)
To (3) are combined, that is, differential pressure oil is supplied to the back pressure chamber from an oil reservoir under the action of the discharge gas pressure through an appropriate throttle oil supply passage, and between the back pressure chamber and the suction chamber (or compression chamber). It is conceivable that the back pressure chamber is restored to the normal pressure by opening the control valve only when the back pressure chamber pressure rises abnormally by communicating the above through the control valve as in (1). By repeatedly opening and closing between the suction chamber (or the compression chamber) and the suction chamber (or compression chamber), the compression load and back pressure chamber pressure change abruptly, fluctuations in load torque, abnormal noise due to orbiting scroll flapping, and back pressure chamber There is an important problem that the original low vibration and low noise characteristics of the scroll compressor are impaired by the gas blow-through noise generated when the gas blows into the suction chamber (or the compression chamber). On the other hand, as a measure for preventing the pressure in the back pressure chamber from being abnormally lowered, the configuration of Japanese Patent Application Laid-Open No. 58-160580 has been proposed. This structure is provided with a passage that connects the back pressure chamber and the discharge gas passage side, and when the back pressure chamber pressure becomes lower than the set pressure, the control valve in the middle of the passage is opened to discharge the high pressure gas from the discharge gas passage side. Is introduced into the back pressure chamber so that the back pressure chamber pressure is controlled not to become too low. However, even in this configuration, as in the case of Japanese Patent Laid-Open No. 57-76291, no consideration is given to always ensuring the amount of oil supplied to the back pressure chamber, and there is the same problem as described above. Therefore, the present invention controls the back pressure chamber pressure by continuously changing the opening degree of the throttle passage between the back pressure chamber and the suction chamber (or the compression chamber) in the middle of the fuel supply passage, thereby reducing the vibration and noise. It is intended to provide a scroll compressor having excellent characteristics and durability.
【０００４】[0004]
【課題を解決するための手段】上記問題を解決するため
に本発明のスクロール圧縮機は、吐出ガス圧力の作用す
る潤滑油供給元，旋回スクロールの背圧室，吸入室（ま
たは圧縮室）を順次経由する給油通路を備え、前記給油
通路途中の背圧室と吸入室（または圧縮室）との間に給
油通路制御装置を配置し、給油通路制御装置は背圧室と
吸入室（または圧縮室）との間の圧力差を設定範囲内に
制御すべく、その絞り通路の開度を連続的に変化させる
開度調整機能を備えたものである。In order to solve the above problems, a scroll compressor according to the present invention has a lubricating oil supply source on which discharge gas pressure acts, a back pressure chamber of an orbiting scroll, and a suction chamber (or compression chamber). An oil supply passage that sequentially passes is provided, and an oil supply passage control device is arranged between the back pressure chamber and the suction chamber (or compression chamber) in the middle of the oil supply passage. In order to control the pressure difference between the chamber and the chamber within a set range, it is provided with an opening adjustment function for continuously changing the opening of the throttle passage.
【０００５】[0005]
【作用】本発明は上記構成によって、圧縮機冷時始動直
後しばらくの間は、吐出圧力が低いので潤滑油供給元か
ら背圧室に流入する潤滑油の圧力も低いので、給油通路
制御装置の絞り通路の開度は小さく、背圧室から吸入室
（または圧縮室）に流出する潤滑油量を少なくする。そ
れによって、背圧室の圧力上昇を早め、早期背圧設定に
より旋回スクロールを早期に安定させ、背圧不足に起因
する旋回スクロールのバタ付きを防ぎ、異常音の発生や
摺動部の異常摩耗を防止する。また、始動後の時間経過
と共に吐出ガスが上昇し、潤滑油供給元から背圧室に流
入する潤滑油の圧力上昇に伴い、給油通路制御装置はそ
の絞り通路の開度を徐々に広げて背圧室から吸入室（ま
たは圧縮室）に流出する潤滑油量を増加させ、背圧室圧
力を設定範囲内に制御し、固定スクロールに対する旋回
スクロールの安定した適正押圧力を維持し、負荷変動の
少ない静粛運転を継続させる。With the above structure, the discharge pressure is low for a while immediately after the cold start of the compressor, so that the pressure of the lubricating oil flowing into the back pressure chamber from the lubricating oil supply source is also low. The opening of the throttle passage is small, and the amount of lubricating oil flowing from the back pressure chamber to the suction chamber (or compression chamber) is reduced. This accelerates the pressure rise in the back pressure chamber, stabilizes the orbiting scroll early by setting the early back pressure, prevents the orbiting scroll from flapping due to insufficient back pressure, and produces abnormal noise and abnormal wear of sliding parts. Prevent. In addition, as the discharge gas rises with the lapse of time after the start of the engine and the pressure of the lubricating oil flowing from the lubricating oil source to the back pressure chamber rises, the oil supply passage control device gradually widens the opening of the throttle passage to increase the back pressure. The amount of lubricating oil flowing from the pressure chamber to the suction chamber (or compression chamber) is increased, the back pressure chamber pressure is controlled within the set range, and the stable proper pressing force of the orbiting scroll with respect to the fixed scroll is maintained, and the load fluctuation Continue low quiet operation.
【０００６】[0006]
【実施例】以下、本発明の一実施例のスクロール圧縮機
について、図面を参照しながら説明する。図１は本発明
の一実施例におけるスクロール冷媒圧縮機の縦断面図、
図２は図１におけるＡ部の詳細説明図を示すものであ
る。図１において、１は密閉シェル、２は密閉シェル１
に圧入固定された本体フレーム、３，４は本体フレーム
２の中心部に設けられた軸受、５は軸受３，４に支承さ
れ貫通した油穴６と軸受４に対向した位置に油穴６と連
通して油穴７を設けた駆動軸で、その上端には偏心軸部
８が設けられ下端は密閉シェル１の底部の油溜９にまで
伸びて没入している。１０はモータでその回転子１１は
駆動軸５に、固定子１２は密閉シェル１に圧入固定され
ている。偏心軸部８に連結し、その中心に軸受部１３を
備えた旋回スクロール１４のラップ支持円盤１５はその
上面に直立した旋回スクロールラップ１６が一体的に形
成され、その下面は本体フレーム２の上端開口穴に突出
したスラスト軸受座１７に支承されている。旋回スクロ
ールラップ１６は、その平面形状がうず巻き状をなし、
その縦断面は矩形をなして隣り合う旋回スクロールラッ
プ１６は平行関係にある。自転阻止用のオルダムリング
１８は、平らなリングの両面に互いに直交する平行キー
形状のキー部を備えたもので、ラップ支持円盤１５とス
ラスト軸受座１７との間に設けられている。このオルダ
ムリング１８の上面側のキー部はラップ支持円盤１５の
背面に設けられたキー溝（図示せず）に、下面側のキー
部はスラスト軸受座１７に設けられたキー溝１９にはめ
込まれており、駆動軸５の回転によってラップ支持円盤
１５の軸受部１３は駆動軸５の軸心の回りに円運動をな
し、旋回スクロールラップ１６は旋回運動する。また、
本体フレーム２の上端面には上端開口穴をふさいでラッ
プ支持円盤１５の背圧室２０とした固定スクロール３４
の鏡板２１がスラスト軸受座１７と共に旋回スクロール
１４を微少隙間で挟むように取付られている。背圧室２
０はラップ支持円盤１５によって仕切られ、その外周面
の背圧室２０ａと背面側の背圧室２０ｂに分けられてい
る。鏡板２１にはその内側に環状の吸入室２２が設けら
れ、さらにその内側には旋回スクロール１６に平行で同
形状寸法の固定スクロールラップ２３のうず巻きの中心
には密閉シェル１の内側を吐出空間２４とした吐出ポー
ト２５が設けられ、ラップ支持円盤１５との摺動面に開
口して吸入室２２と背圧室２０ａを連通する細穴のバラ
ンス通路２６と背圧室２０ａと背圧室２０ｂを連通する
細穴のバランス通路２７とが鏡板２１とスラスト軸受座
１７に設けられ、ラップ支持円盤１５が所定の旋回角度
範囲（圧縮室が吸入行程である）にあるときのみ連通す
るようにそれぞれ配置され、バランス通路２６の途中に
は図２に示すように鏡板２１にケース４０が圧入されて
バランス通路２６の両端開口部を挟めるように構成さ
れ、その通路の中央部の上流側には鋼球４１が、下流側
にはコイルバネ４２が装着されて給油通路制御装置４３
を構成し、コイルバネ４２は背圧室２０と吸入室２２と
の間の圧力差に基づいて鋼球４１に作用する背圧力に対
抗して鋼球４１を移動させ、バランス通路２６の開度を
連続的に変化させるべく、鋼球４１を常時付勢してい
る。また、環状の吸入室２２には側方より密閉シェル１
を貫通した吸入管２８が接続され、密閉シェル１の上面
には密閉シェル１の内側面に向かって開口した吐出管２
９が接続されている。密閉シェル１に圧入固定された本
体フレーム２の外側面には溝３０が設けられ、この溝３
０が密閉シェル１の鏡板２１の側の吐出空間２４とモー
タ１０の側とを連通している。以上のように構成された
スクロール冷媒圧縮機について、以下図１および図２を
用いてその動作を説明する。まず図１はスクロール冷媒
圧縮機の縦断面図、図２は図１におけるバランス通路２
６の近傍Ａ部の詳細図であって、モータ１０によって回
転子１１が回転し、駆動軸５が回転駆動されると旋回ス
クロール１４が旋回運動をし、吸入管２８を通して冷媒
ガスが吸入室２２に吸入され、この冷媒ガスは旋回スク
ロールラップ１６と固定スクロールラップ２３の間に形
成された圧縮室内に閉じ込められ、旋回スクロールラッ
プ１６の旋回運動に伴って圧縮され、吐出ポート２５よ
り吐出空間２４へ吐出され、冷媒ガス中に含まれる潤滑
油の一部はその自重などによって冷媒ガスから分離して
密閉シェル１と本体フレーム２との間の溝３０などを経
て底部の油溜９に収集され、残りの潤滑油は吐出冷媒ガ
スと共に吐出管２９を経て外部の冷凍サイクルへ搬出さ
れる。一方、固定スクロール３４の鏡板２１と本体フレ
ーム２とによって吐出空間２４から隔離されて形成され
た背圧室２０を経由する高圧側の油溜９から低圧側の吸
入室２２までの差圧給油は次のようにして行われる。す
なわち、圧縮機冷時始動後しばらくの間は、背圧室２０
と吸入室２２との間の圧力差が小さく、バランス通路２
６の開度は最少状態に絞られている。吐出冷媒ガスで充
満された密閉シェル１の底部の油溜９の粘性の低い潤滑
油は駆動軸５に設けられた油穴６、７と駆動軸５を支承
する軸受３、４や偏心軸部８の軸受部１３の微少隙間を
通過することによって漸次減圧され吸入室力と吐出圧力
との中間圧力の状態で背圧室２０ｂに供給される。さら
に潤滑油は、旋回スクロール１４のラップ支持円盤１５
の旋回運動によって間欠的に開閉する細穴のバランス通
路２７を経て背圧室２０ａに間欠給油される。背圧室２
０ａの圧力上昇に伴い、バランス通路２６の開度が徐々
に広がり、背圧室２０ａの潤滑油は吸入室２２に少量づ
つ間欠給油され、吸入冷媒ガスと共に再び圧縮，吐出さ
れる。圧縮機始動後の時間経過と共に吐出圧力が上昇
し、油溜９から軸受３，４，軸受部１３を経由して背圧
室２０に流入する潤滑油量が増し、背圧室２０の圧力も
上昇する。背圧室２０と吸入室２２との間の圧力差を設
定範囲内に制御すべく給油通路制御装置はその絞り通路
の開度を徐々に広げ、油溜９から吸入室２２に流入する
潤滑油量が徐々に増加する。この差圧給油方式によれ
ば、ラップ支持円盤１５の背面の背圧室２０の圧力を給
油通路の通路抵抗調整によって吐出圧力に近い状態から
吸入圧力に近い状態にまで自由に設定できるので、ラッ
プ支持円盤１５の背面に作用するガス圧荷重と圧縮室内
のガス圧荷重との荷重差を自由に調整でき、それによっ
てラップ支持円盤１５を鏡板２１の側へ押しつけること
も、また、鏡板２１から離してスラスト軸受座１７の側
に押しつけることもできる。本実施例では定常運転時な
ど潤滑油の粘性が低い場合のラップ支持円盤１５は鏡板
２１の側へスラスト力が作用するように、また、冷時起
動直後など潤滑油の粘性が高い場合のラップ支持円盤１
５はスラスト軸受座１７の側へスラスト力が作用するよ
うにバランス通路２６の通路抵抗が調整されて給油通路
制御装置の機能を備えている。また、このスクロール冷
媒圧縮機をヒートポンプ式冷凍サイクルに組み込み、暖
房運転冷媒サイクルから除霜運転冷凍サイクルに切り換
えた直後、吐出室圧力が低圧状態に、吸入室圧力が高圧
状態になる関係上、冷媒ガスが吸入室２２から背圧室２
０にバランス通路２７，２７を介して逆流しようとする
が、バランス通路２６に設けた鋼球４１が通路を閉じ、
冷媒ガスが背圧室２０を経由して油溜９に逆流するのを
阻止し、背圧室２０や軸受摺動面の潤滑油流出と摺動面
の焼付きを防ぐ。なお、本実施例ではバランス通路２６
の下流側の開口穴がコイルバネ４２の端部に連通してい
る構成であったが、図３に示すようにコイルバネ４２の
中央部付近または鋼球４１の側付近に連通する構成でも
よい。また上記実施例では、背圧室２０の給油通路下流
側を吸入室としたが、図７の場合と同様に、背圧室２０
の給油通路下流側を圧縮行程中の圧縮室にしても良く、
その給油通路途中に図２と同様の給油通路制御装置を設
けても良い。なお、この給油通路構成における給油通路
制御装置は以下に述べる逆止弁作用も兼ねる。すなわ
ち、圧縮機冷時始動直後などは、圧縮機外部配管系に連
通する吐出室の圧力が低く、油溜９から背圧室２０への
潤滑油流入が少ないので、背圧室２０の圧力が背圧室２
０に連通する圧縮室の圧力よりも間欠的に低い場合があ
る。このため、圧縮途中の冷媒ガスが背圧室２０に流入
しようとするが、給油通路制御装置の逆止弁作用により
背圧室２０から油溜９への給油通路の冷媒ガス吹き抜け
に伴う潤滑油流出とそれに伴う摺動部焼付きを防ぐ。ま
た、圧縮途中に冷媒液や多量の潤滑油を圧縮することに
起因して生じる圧縮室瞬時異常圧力上昇（液圧縮現象）
時に冷媒ガスが背圧室２０に逆流することも防ぐ。その
ことによって、背圧室２０の圧力上昇と旋回スクロール
１４への背圧付勢力増加を阻止し、旋回スクロール１４
を固定スクロール３４から軸方向に離反させ、圧縮室圧
力を急低下して過負荷軽減作用を行わせることもでき
る。以上のように上記実施例によれば、吐出ガス圧力の
作用する油溜９，駆動軸５に設けられた油穴６，７と駆
動軸５を支承する軸受３，４や偏心軸部８の軸受部１３
の微少隙間，旋回スクロール１４の背圧室（背圧室２０
ｂ，背圧室２０ａ），吸入室２２を順次経由する給油通
路を備え、その給油通路途中の背圧室２０と吸入室２２
との間の鏡板２１に設けられた細穴部を有するバランス
通路２６に鋼球４１の弁体とそれを上流側に向かって付
勢するコイルバネ４２とから成る給油通路制御弁装置４
３を配置し、給油通路制御弁装置４３は背圧室２０と吸
入室２２との間の圧力差を設定範囲内に制御すべく、バ
ランス通路２６の上流側通路の開度を連続的に変化させ
ることのできる開度調整機構を備えたことにより、圧縮
機冷時始動直後しばらくの間は吐出圧力が低く、油溜９
から背圧室２０に流入する潤滑油の圧力が低くとも給油
通路制御装置４３の絞り通路の開度が小さいので背圧室
２０から吸入室２２に流出する潤滑油量を最少にし、そ
れによって背圧室２０の潤滑油確保と圧力上昇を早める
ことができる。その結果、起動初期の吸入圧力が高いこ
とに起因して過大となり旋回スクロール１４およびスラ
スト軸受座１７に作用するスラスト荷重を背圧力で軽減
すると共に、スラスト軸受座１７への早期給油によって
摺動部耐久性の低下を防ぐことができる。また背圧室２
０の圧力設定立ち上がりが早く、背圧力不安定に起因す
る旋回スクロール１４の傾きや軸方向移動などのバタ付
きを防ぎ、異常音発生，摺動部耐久性を防止することが
できる。また、始動後の時間経過と共に吐出圧力が上昇
し、吸入圧力が低下し、それに伴って背圧室２０が設定
圧力に達した後は、背圧室２０から吸入室２２に排出す
る潤滑油量を連続的に制御するので、吐出圧力が異常圧
力上昇した場合でもそれに追従して適正背圧ができ、圧
縮負荷変動や背圧変動を少なくして安定した圧縮機運転
を継続させことができる。DESCRIPTION OF THE PREFERRED EMBODIMENTS A scroll compressor according to an embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a vertical sectional view of a scroll refrigerant compressor according to an embodiment of the present invention,
FIG. 2 is a detailed explanatory diagram of the portion A in FIG. In FIG. 1, 1 is a closed shell, 2 is a closed shell 1
The main body frame is press-fitted into the main body frame 3, 3 and 4 are bearings provided in the central portion of the main body frame 2, and 5 is an oil hole 6 supported by the bearings 3 and 4 and an oil hole 6 at a position facing the bearing 4. An eccentric shaft portion 8 is provided at the upper end of the drive shaft, which communicates with the oil hole 7, and the lower end extends into the oil reservoir 9 at the bottom of the closed shell 1 and is immersed therein. Reference numeral 10 denotes a motor, a rotor 11 of which is fixed to the drive shaft 5 and a stator 12 of which is fixed to the hermetic shell 1 by press fitting. The wrap support disk 15 of the orbiting scroll 14 which is connected to the eccentric shaft portion 8 and has the bearing portion 13 at the center thereof is integrally formed with the orbiting scroll wrap 16 which is upright on the upper surface thereof, and the lower surface thereof is the upper end of the main body frame 2. It is supported by a thrust bearing seat 17 protruding into the opening hole. The orbiting scroll wrap 16 has a spiral shape in a plan view,
The vertical cross section is rectangular and adjacent orbiting scroll wraps 16 are parallel to each other. The rotation-preventing Oldham ring 18 is provided with parallel key-shaped key portions orthogonal to each other on both sides of a flat ring, and is provided between the lap support disk 15 and the thrust bearing seat 17. The key portion on the upper surface side of the Oldham ring 18 is fitted in the key groove (not shown) provided on the back surface of the lap support disk 15, and the key portion on the lower surface side is fitted in the key groove 19 provided in the thrust bearing seat 17. The rotation of the drive shaft 5 causes the bearing portion 13 of the wrap support disk 15 to make a circular motion around the axis of the drive shaft 5, and the orbiting scroll wrap 16 makes an orbiting motion. Also,
A fixed scroll 34 is formed as a back pressure chamber 20 of the lap support disk 15 by closing an upper end opening hole in the upper end surface of the main body frame 2.
The end plate 21 is attached together with the thrust bearing seat 17 so as to sandwich the orbiting scroll 14 with a minute gap. Back pressure chamber 2
0 is divided by a lap support disk 15 and is divided into a back pressure chamber 20a on the outer peripheral surface thereof and a back pressure chamber 20b on the back surface side. An annular suction chamber 22 is provided inside the end plate 21, and the inside of the closed shell 1 is discharged at the center of the spiral of a fixed scroll wrap 23 that is parallel to the orbiting scroll 16 and has the same shape. The discharge port 25 is provided to open the sliding surface with the lap support disk 15 and connect the suction passage 22 and the back pressure chamber 20a to each other through a balance passage 26 of a small hole, the back pressure chamber 20a and the back pressure chamber 20b. A fine hole balance passage 27 communicating with each other is provided in the end plate 21 and the thrust bearing seat 17, and is arranged so as to communicate with each other only when the lap support disk 15 is in a predetermined swing angle range (the compression chamber is in the suction stroke). As shown in FIG. 2, the case 40 is press-fitted into the end plate 21 in the middle of the balance passage 26 so as to sandwich the openings at both ends of the balance passage 26. The flow side steel balls 41, the oil supply passage control device coil spring 42 is mounted on the downstream side 43
The coil spring 42 moves the steel ball 41 against the back pressure acting on the steel ball 41 on the basis of the pressure difference between the back pressure chamber 20 and the suction chamber 22 to adjust the opening degree of the balance passage 26. The steel ball 41 is constantly urged so as to be continuously changed. In addition, the annular suction chamber 22 has a closed shell 1 from the side.
Is connected to a suction pipe 28, and the upper surface of the closed shell 1 is provided with a discharge pipe 2 opening toward the inner side surface of the closed shell 1.
9 is connected. A groove 30 is provided on the outer surface of the body frame 2 press-fitted and fixed to the closed shell 1.
Reference numeral 0 connects the discharge space 24 on the end plate 21 side of the closed shell 1 to the motor 10 side. The operation of the scroll refrigerant compressor configured as described above will be described below with reference to FIGS. 1 and 2. First, FIG. 1 is a vertical sectional view of a scroll refrigerant compressor, and FIG. 2 is a balance passage 2 in FIG.
6 is a detailed view of a portion A in the vicinity of 6, wherein the orbiting scroll 14 orbits when the rotor 11 is rotated by the motor 10 and the drive shaft 5 is rotationally driven, and the refrigerant gas passes through the suction pipe 28 and the suction chamber 22. The refrigerant gas is drawn into the compression chamber formed between the orbiting scroll wrap 16 and the fixed scroll wrap 23, is compressed by the orbiting motion of the orbiting scroll wrap 16, and is discharged from the discharge port 25 to the discharge space 24. A part of the lubricating oil discharged and contained in the refrigerant gas is separated from the refrigerant gas by its own weight and the like, and is collected in the bottom oil sump 9 through the groove 30 between the closed shell 1 and the main body frame 2, The remaining lubricating oil is discharged to the external refrigeration cycle through the discharge pipe 29 together with the discharge refrigerant gas. On the other hand, the differential pressure oil supply from the high pressure side oil reservoir 9 to the low pressure side suction chamber 22 via the back pressure chamber 20 formed by being separated from the discharge space 24 by the end plate 21 of the fixed scroll 34 and the main body frame 2 is performed. This is done as follows. That is, the back pressure chamber 20 is kept for a while after the cold start of the compressor.
And the pressure difference between the suction chamber 22 and the balance passage 2 is small.
The opening degree of 6 is narrowed to the minimum state. The low-viscosity lubricating oil in the oil reservoir 9 at the bottom of the closed shell 1 filled with the discharged refrigerant gas is provided with the oil holes 6 and 7 provided in the drive shaft 5 and the bearings 3 and 4 supporting the drive shaft 5 and the eccentric shaft portion. The pressure is gradually reduced by passing through the minute gap of the bearing 13 of No. 8 and is supplied to the back pressure chamber 20b in a state of an intermediate pressure between the suction chamber force and the discharge pressure. Further, the lubricating oil is the lap support disk 15 of the orbiting scroll 14.
Oil is intermittently supplied to the back pressure chamber 20a through the balance passage 27 having a small hole which is opened and closed intermittently by the turning motion of the. Back pressure chamber 2
As the pressure of 0a increases, the opening degree of the balance passage 26 gradually expands, and the lubricating oil in the back pressure chamber 20a is intermittently supplied to the suction chamber 22 little by little, and is compressed and discharged again together with the suction refrigerant gas. The discharge pressure rises with the lapse of time after the start of the compressor, the amount of lubricating oil flowing from the oil reservoir 9 into the back pressure chamber 20 via the bearings 3, 4 and the bearing portion 13 increases, and the pressure in the back pressure chamber 20 also increases. To rise. In order to control the pressure difference between the back pressure chamber 20 and the suction chamber 22 within a set range, the oil supply passage control device gradually expands the opening of the throttle passage, and the lubricating oil flowing from the oil reservoir 9 into the suction chamber 22 is reached. The amount gradually increases. According to this differential pressure oil supply system, the pressure of the back pressure chamber 20 on the back surface of the lap support disk 15 can be freely set from the state close to the discharge pressure to the state close to the suction pressure by adjusting the passage resistance of the oil supply passage. The load difference between the gas pressure load acting on the back surface of the support disk 15 and the gas pressure load in the compression chamber can be freely adjusted, so that the lap support disk 15 can be pressed toward the end plate 21 or separated from the end plate 21. It can also be pressed against the thrust bearing seat 17 side. In the present embodiment, the lap support disk 15 in the case where the viscosity of the lubricating oil is low, such as during steady operation, acts so that the thrust force acts on the end plate 21 side, and in the case where the viscosity of the lubricating oil is high, such as immediately after cold start, Support disk 1
5 has a function of an oil supply passage control device in which the passage resistance of the balance passage 26 is adjusted so that the thrust force acts on the thrust bearing seat 17 side. In addition, this scroll refrigerant compressor is incorporated into a heat pump type refrigeration cycle, and immediately after switching from the heating operation refrigerant cycle to the defrosting operation refrigeration cycle, the discharge chamber pressure becomes a low pressure state, and the suction chamber pressure becomes a high pressure state. Gas from the suction chamber 22 to the back pressure chamber 2
0 tries to flow back to 0 through the balance passages 27, 27, but the steel ball 41 provided in the balance passage 26 closes the passage.
Refrigerant gas is prevented from flowing back into the oil reservoir 9 via the back pressure chamber 20, and the outflow of lubricating oil from the back pressure chamber 20 and the bearing sliding surface and seizure of the sliding surface are prevented. In this embodiment, the balance passage 26
Although the downstream opening hole is communicated with the end portion of the coil spring 42, it may be communicated with the vicinity of the central portion of the coil spring 42 or the steel ball 41 side as shown in FIG. Further, in the above embodiment, the suction chamber is located on the downstream side of the oil supply passage of the back pressure chamber 20, but as in the case of FIG.
The downstream side of the oil supply passage may be used as the compression chamber during the compression stroke,
An oil supply passage control device similar to that of FIG. 2 may be provided in the oil supply passage. The oil supply passage control device in this oil supply passage configuration also has a check valve function described below. That is, immediately after the compressor is started when the compressor is cold, the pressure of the discharge chamber communicating with the compressor external piping system is low, and the amount of lubricating oil flowing from the oil reservoir 9 into the back pressure chamber 20 is small. Back pressure chamber 2
It may be intermittently lower than the pressure of the compression chamber communicating with zero. For this reason, the refrigerant gas in the middle of compression tends to flow into the back pressure chamber 20, but the check valve action of the oil supply passage control device causes the lubricating oil accompanying the blowout of the refrigerant gas in the oil supply passage from the back pressure chamber 20 to the oil reservoir 9. Prevents outflow and seizure of sliding parts. In addition, instantaneous abnormal pressure rise in the compression chamber (liquid compression phenomenon) that occurs due to compression of the refrigerant liquid and a large amount of lubricating oil during compression.
It also prevents the refrigerant gas from flowing back to the back pressure chamber 20. As a result, an increase in pressure in the back pressure chamber 20 and an increase in back pressure biasing force on the orbiting scroll 14 are prevented, and the orbiting scroll 14 is prevented.
Can be separated from the fixed scroll 34 in the axial direction, and the pressure in the compression chamber can be drastically reduced to perform an overload reducing action. As described above, according to the above-described embodiment, the oil sump 9 on which the discharge gas pressure acts, the oil holes 6 and 7 provided in the drive shaft 5, the bearings 3 and 4 supporting the drive shaft 5, and the eccentric shaft portion 8 are formed. Bearing part 13
Of the back pressure chamber of the orbiting scroll 14 (back pressure chamber 20
b, the back pressure chamber 20a), and the suction chamber 22 are provided in sequence, and the back pressure chamber 20 and the suction chamber 22 are provided in the middle of the lubrication passage.
Between the oil passage control valve device 4 including a valve body of a steel ball 41 and a coil spring 42 for urging the valve body toward the upstream side in a balance passage 26 having a narrow hole portion provided in the end plate 21 between
3, the oil supply passage control valve device 43 continuously changes the opening degree of the upstream passage of the balance passage 26 so as to control the pressure difference between the back pressure chamber 20 and the suction chamber 22 within a set range. Since the opening adjustment mechanism that can be operated is provided, the discharge pressure is low for a while immediately after the compressor is started when the compressor is cold, and the oil sump 9
Even if the pressure of the lubricating oil flowing from the back pressure chamber 20 to the back pressure chamber 20 is low, the opening of the throttle passage of the oil supply passage control device 43 is small, so that the amount of lubricating oil flowing from the back pressure chamber 20 to the suction chamber 22 is minimized, thereby reducing the back pressure. It is possible to secure the lubricating oil in the pressure chamber 20 and accelerate the pressure rise. As a result, the thrust pressure acting on the orbiting scroll 14 and the thrust bearing seat 17 becomes excessive due to the high suction pressure at the initial stage of startup, and the thrust pressure seat 17 reduces the thrust load. It is possible to prevent deterioration of durability. Back pressure chamber 2
It is possible to prevent the fluttering of the orbiting scroll 14 from tilting or moving in the axial direction due to unstable back pressure, and prevent abnormal noise and durability of the sliding portion. In addition, the discharge pressure increases and the suction pressure decreases with the lapse of time after the start, and accordingly, after the back pressure chamber 20 reaches the set pressure, the amount of lubricating oil discharged from the back pressure chamber 20 to the suction chamber 22. Is controlled continuously, even if the discharge pressure rises to an abnormal pressure, the back pressure can be appropriately tracked accordingly, and fluctuations in compression load and fluctuations in back pressure can be reduced and stable compressor operation can be continued.
【０００７】[0007]
【発明の効果】以上のように本発明は、吐出ガス圧力の
作用する潤滑油供給元，背圧室，吸入室（または圧縮
室）を順次経由する給油通路を備え、給油通路途中の背
圧室と吸入室（または圧縮室）との間に給油通路制御装
置を配置し、給油通路制御装置は、背圧室と吸入室（ま
たは圧縮室）との間の圧力差を設定範囲内に制御すべ
く、その絞り通路の開度を連続的に変化させる開度調整
機構を備えたことにより、圧縮機冷時始動直後の吐出圧
力が低く、潤滑油供給元から背圧室２０に流入する潤滑
油の圧力が比較的低い場合でも、給油通路制御装置の絞
り通路の開度が小さいので背圧室から吸入室に流出する
潤滑油量を少なくでき、それによって背圧室の潤滑油充
満と圧力上昇を早めることができる。その結果、背圧室
の圧力設定立ち上がりを早め、背圧力不安定に起因する
旋回スクロールの固定スクロールおよび駆動軸に対する
傾き、軸方向移動などのバタ付きを油膜の緩衡作用で防
ぎ、摺動部からの異常音発生，摩耗を防止して耐久性を
向上させることができる。また、吐出圧力が上昇し、そ
れに追従して背圧室と吸入室（または圧縮室）との間の
差圧が設定範囲に達した後は、背圧室から吸入室（また
は圧縮室）に排出する潤滑油量を連続的に制御するの
で、ガスや潤滑油の断続的な排出音もなく、吐出圧力が
異常圧力上昇した場合でもそれに追従して背圧室圧力を
連続的に適正範囲に制御して、圧縮負荷や背圧の急変動
を少なくし、低振動，低騒音運転を実現できる数多くの
優れた効果を奏するものである。As described above, according to the present invention, the lubricating oil supply source, the back pressure chamber, and the suction chamber (or the compression chamber), which are subjected to the discharge gas pressure, are sequentially provided, and the back pressure in the middle of the oil supply passage is provided. The oil supply passage control device is arranged between the suction chamber (or the compression chamber) and the suction chamber, and the oil supply passage control device controls the pressure difference between the back pressure chamber and the suction chamber (or the compression chamber) within the set range. Therefore, by providing an opening degree adjusting mechanism that continuously changes the opening degree of the throttle passage, the discharge pressure immediately after the compressor is started cold is low, and the lubricating oil that flows into the back pressure chamber 20 from the lubricating oil source is provided. Even when the oil pressure is relatively low, the opening of the throttle passage of the oil supply passage control device is small, so the amount of lubricating oil flowing out from the back pressure chamber to the suction chamber can be reduced, which allows the back pressure chamber to be filled with lubricating oil You can accelerate the rise. As a result, the pressure setting rise of the back pressure chamber is accelerated, and flapping of the orbiting scroll with respect to the fixed scroll and the drive shaft due to unstable back pressure, axial movement, etc. is prevented by the oil film straining action, and the sliding part is prevented. It is possible to improve the durability by preventing abnormal noise from being generated and abrasion. Also, after the discharge pressure rises and the differential pressure between the back pressure chamber and the suction chamber (or compression chamber) reaches the set range following the rise, the back pressure chamber moves to the suction chamber (or compression chamber). Since the amount of lubricating oil to be discharged is controlled continuously, there is no intermittent discharge noise of gas or lubricating oil, and even if the discharge pressure rises abnormally, the back pressure chamber pressure is continuously adjusted to an appropriate range by following it. By controlling, it is possible to reduce sudden changes in compression load and back pressure and to achieve a number of excellent effects that can realize low vibration and low noise operation.
【図１】本発明の第１の実施例におけるスクロール冷媒
圧縮機の縦断面図FIG. 1 is a vertical sectional view of a scroll refrigerant compressor according to a first embodiment of the present invention.
【図２】図１におけるＡ部断面図FIG. 2 is a sectional view of part A in FIG.
【図３】本発明におけるそれぞれ異なる他の実施例を示
すスクロール冷媒圧縮機の部分断面図FIG. 3 is a partial cross-sectional view of a scroll refrigerant compressor showing another embodiment of the present invention.
【図４】本発明におけるそれぞれ異なる他の実施例を示
すスクロール冷媒圧縮機の部分断面図FIG. 4 is a partial cross-sectional view of a scroll refrigerant compressor showing different embodiments of the present invention.
【図５】それぞれ異なる従来のスクロール圧縮機の縦断
面図FIG. 5 is a vertical cross-sectional view of different conventional scroll compressors.
【図６】それぞれ異なる従来のスクロール圧縮機の縦断
面図FIG. 6 is a vertical cross-sectional view of different conventional scroll compressors.
【符号の説明】 １ 密閉シェル ２ 本体フレーム ５ 駆動軸 １０ モータ １４ 旋回スクロール １５ ラップ支持円盤 １６ 旋回スクロールラップ ２０ 背圧室 ２１ 鏡板 ２２ 吸入室 ２３ 固定スクロールラップ ２５ 吐出ポート ２６、２７ バランス通路 ３４ 固定スクロール ４１ 鋼球 ４２ コイルバネ ４３ 給油通路制御装置[Explanation of symbols] 1 closed shell 2 main body frame 5 drive shaft 10 motor 14 orbiting scroll 15 wrap support disk 16 orbiting scroll wrap 20 back pressure chamber 21 end plate 22 suction chamber 23 fixed scroll wrap 25 discharge port 26, 27 balance passage 34 fixed Scroll 41 Steel ball 42 Coil spring 43 Oil supply passage control device
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.5 識別記号 庁内整理番号 ＦＩ 技術表示箇所 Ｆ０４Ｃ 29/02 ３２１ Ａ 6907−3Ｈ 29/06 Ｄ 6907−3Ｈ ─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. 5 Identification number Office reference number FI technical display location F04C 29/02 321 A 6907-3H 29/06 D 6907-3H
Claims (1)
形成されたうず巻状の固定スクロールラップに対して旋
回スクロールの一部をなすラップ支持円盤上の旋回スク
ロールラップをかみ合わせ、前記固定スクロールラップ
の外側には吸入室を形成し、前記ラップ支持円盤は、駆
動軸を支承する本体フレームと前記鏡板との間に形成さ
れかつ前記本体フレームの外側の潤滑油供給元に通じた
前記旋回スクロールの背圧室に遊合状態で配置され、さ
らに前記ラップ支持円盤の自転阻止機構を介して旋回可
能に支承され、前記固定スクロールラップと前記旋回ス
クロールとの間に形成される圧縮室の容積変化を利用し
て流体を圧縮するようにしたスクロール式圧縮機構を形
成し、吐出圧力の作用する前記潤滑油供給元，前記背圧
室，前記吸入室または前記圧縮室を順次経由する給油通
路を備え、前記給油通路途中の前記背圧室と前記吸入室
または前記圧縮室または前記背圧室と前記潤滑油供給元
との間に給油通路制御装置を配置し、前記給油通路制御
装置は、前記背圧室と前記吸入室または前記圧縮室との
間の圧力差を設定範囲内に制御すべく、その絞り通路の
開度を連続的に変化させる開度調整機能を備えたスクロ
ール圧縮機。1. A fixed scroll wrap on a lap support disk which forms a part of an orbiting scroll is engaged with a fixed scroll wrap which is a spiral scroll formed on one surface of an end plate which forms a part of the fixed scroll. A suction chamber is formed on the outside of the wrap, and the wrap support disk is formed between the body frame supporting the drive shaft and the end plate and communicates with a lubricating oil supply source outside the body frame. Of the compression chamber formed between the fixed scroll wrap and the orbiting scroll by being rotatably supported by the lap support disk through a rotation preventing mechanism of the wrap support disk. Is used to form a scroll-type compression mechanism, and the lubricating oil supply source, the back pressure chamber, and the suction chamber, which act on the discharge pressure, are formed. Is provided with an oil supply passage sequentially passing through the compression chamber, and an oil supply passage control device is provided between the back pressure chamber and the suction chamber or the compression chamber or the back pressure chamber and the lubricating oil supply source in the middle of the oil supply passage. The refueling passage control device is arranged to continuously change the opening of the throttle passage so as to control the pressure difference between the back pressure chamber and the suction chamber or the compression chamber within a set range. Scroll compressor with degree adjustment function.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4175187A JP2574599B2 (en) | 1992-07-02 | 1992-07-02 | Scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4175187A JP2574599B2 (en) | 1992-07-02 | 1992-07-02 | Scroll compressor |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14874485A Division JPH0778391B2 (en) | 1985-07-05 | 1985-07-05 | Scroll gas compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH05187369A true JPH05187369A (en) | 1993-07-27 |
| JP2574599B2 JP2574599B2 (en) | 1997-01-22 |
Family
ID=15991808
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4175187A Expired - Lifetime JP2574599B2 (en) | 1992-07-02 | 1992-07-02 | Scroll compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2574599B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2002061285A1 (en) * | 2001-01-29 | 2002-08-08 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| WO2004111462A1 (en) * | 2003-06-12 | 2004-12-23 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| JP2009257340A (en) * | 2009-08-06 | 2009-11-05 | Hitachi Ltd | Scroll compressor |
| CN110985393A (en) * | 2019-10-28 | 2020-04-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Low-backpressure rotary compressor, corresponding oil return pressure drop control method and air conditioner |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55148994A (en) * | 1979-05-09 | 1980-11-19 | Hitachi Ltd | Closed scroll fluid device |
| JPS5776291A (en) * | 1980-10-31 | 1982-05-13 | Hitachi Ltd | Scroll fluid machine |
| JPS5853601A (en) * | 1981-09-28 | 1983-03-30 | Hitachi Ltd | Scroll fluid machine |
| JPS5985710A (en) * | 1982-11-10 | 1984-05-17 | 伊東 靖郎 | Method of kneading and preparing hydraulic substance kneadedmaterial |
| JPS5998704A (en) * | 1982-11-29 | 1984-06-07 | Nitto Electric Ind Co Ltd | Gas separation membrane comprising polyimide |
| JPS59141783A (en) * | 1983-02-02 | 1984-08-14 | Hitachi Ltd | Scroll fluid machine |
| JPS59180094A (en) * | 1983-03-31 | 1984-10-12 | Toshiba Corp | Scroll type compressor |
-
1992
- 1992-07-02 JP JP4175187A patent/JP2574599B2/en not_active Expired - Lifetime
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55148994A (en) * | 1979-05-09 | 1980-11-19 | Hitachi Ltd | Closed scroll fluid device |
| JPS5776291A (en) * | 1980-10-31 | 1982-05-13 | Hitachi Ltd | Scroll fluid machine |
| JPS5853601A (en) * | 1981-09-28 | 1983-03-30 | Hitachi Ltd | Scroll fluid machine |
| JPS5985710A (en) * | 1982-11-10 | 1984-05-17 | 伊東 靖郎 | Method of kneading and preparing hydraulic substance kneadedmaterial |
| JPS5998704A (en) * | 1982-11-29 | 1984-06-07 | Nitto Electric Ind Co Ltd | Gas separation membrane comprising polyimide |
| JPS59141783A (en) * | 1983-02-02 | 1984-08-14 | Hitachi Ltd | Scroll fluid machine |
| JPS59180094A (en) * | 1983-03-31 | 1984-10-12 | Toshiba Corp | Scroll type compressor |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2002061285A1 (en) * | 2001-01-29 | 2002-08-08 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| US6935852B2 (en) | 2001-01-29 | 2005-08-30 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor having a back pressure chamber comprising high and middle pressure chambers |
| WO2004111462A1 (en) * | 2003-06-12 | 2004-12-23 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| US7458789B2 (en) | 2003-06-12 | 2008-12-02 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| JP2009257340A (en) * | 2009-08-06 | 2009-11-05 | Hitachi Ltd | Scroll compressor |
| CN110985393A (en) * | 2019-10-28 | 2020-04-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Low-backpressure rotary compressor, corresponding oil return pressure drop control method and air conditioner |
| CN110985393B (en) * | 2019-10-28 | 2021-11-16 | 珠海格力节能环保制冷技术研究中心有限公司 | Low-backpressure rotary compressor, corresponding oil return pressure drop control method and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2574599B2 (en) | 1997-01-22 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |