JP2010180703A - Scroll compressor - Google Patents
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- JP2010180703A JP2010180703A JP2009022135A JP2009022135A JP2010180703A JP 2010180703 A JP2010180703 A JP 2010180703A JP 2009022135 A JP2009022135 A JP 2009022135A JP 2009022135 A JP2009022135 A JP 2009022135A JP 2010180703 A JP2010180703 A JP 2010180703A
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本発明は、例えば冷暖房空調装置や冷蔵庫等の冷却装置、あるいはヒートポンプ式の給湯装置等において冷媒ガスを圧縮するためのスクロール圧縮機に関する。 The present invention relates to a scroll compressor for compressing refrigerant gas in a cooling device such as a cooling / heating air conditioner or a refrigerator, or a heat pump type hot water supply device.
従来、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、鏡板から渦巻き状のラップが立ち上がる固定スクロール及び旋回スクロール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作動流体の吸入、圧縮、吐出を行うものである。 Conventionally, scroll compressors used in refrigeration air conditioners and refrigerators generally have fixed scrolls and swirl scrolls, in which spiral wraps rise from end plates, form compression chambers between the two, and orbiting scrolls are constrained by rotation. When rotating along a circular orbit under the restraint of rotation due to, the working fluid is sucked, compressed and discharged by moving while changing its volume.
作動流体は旋回スクロールの旋回運動に伴い徐々に圧縮され、中心部に向かうに従い高圧状態となるため、旋回スクロールには固定スクロールから引き離される方向に離反力が働く。その結果、旋回スクロールと固定スクロールには隙間が生じるため、圧縮途中の漏れが発生し、性能悪化を引き起こしてしまう。この対策として、旋回スクロールの背面に設けた背圧室に中間圧力を印加させ、固定スクロールからの離反を防止している。 The working fluid is gradually compressed along with the turning motion of the orbiting scroll, and becomes a high pressure state toward the center portion. As a result, a gap is generated between the orbiting scroll and the fixed scroll, so that leakage occurs during compression, resulting in performance deterioration. As a countermeasure, an intermediate pressure is applied to a back pressure chamber provided on the back surface of the orbiting scroll to prevent separation from the fixed scroll.
さらに、背圧室に開口する背圧室側開口端から圧縮室に開口する圧縮室側開口端へ連通する経路を備え、旋回スクロールの端板に設けられた圧縮室側開口端が旋回スクロールの旋回運動に伴い、固定スクロールのスラスト面と吸入口に連通する圧縮室を周期的に移動することで、吸入口に連通せず、かつ旋回スクロールの外側に形成される圧縮室に間欠的に給油可能であり、給油されたオイルがこの圧縮室のシールの役割を果たし、作動流体の漏れが抑えられ、圧縮効率の低下を抑制している（例えば、特許文献１参照）。
しかし、上記従来技術では、背圧室と圧縮室を連通させる経路の圧縮室側開口端を、旋回スクロールの内側に形成される圧縮室には開口させていなかったため、この圧縮室には十分なシールオイルが供給されにくく、作動流体の漏れによる圧縮効率の低下が発生する場合があった。 However, in the above prior art, the compression chamber side opening end of the path connecting the back pressure chamber and the compression chamber is not opened in the compression chamber formed inside the orbiting scroll. It is difficult to supply the seal oil, and the compression efficiency may be reduced due to leakage of the working fluid.
特に、上記従来技術に示すような、旋回スクロールの渦巻き状のラップの外壁側に形成される外側圧縮室と内壁側に形成される内側圧縮室の吸入容積が異なる渦巻き状のラップを有するスクロール圧縮機（以後、非対称スクロール圧縮機と称する）においては、渦巻きラップ側面を介した漏れに関して言えば、内側圧縮室から一つ低圧側の内側圧縮室への漏れは、外側圧縮室から一つ低圧側の外側圧縮室への漏れよりも多くなる。 In particular, as shown in the above prior art, scroll compression having spiral wraps with different suction volumes of the outer compression chamber formed on the outer wall side of the spiral wrap of the orbiting scroll and the inner compression chamber formed on the inner wall side. In the compressor (hereinafter referred to as an asymmetric scroll compressor), the leakage from the inner compression chamber to the inner compression chamber on the one low pressure side is from the outer compression chamber on the lower pressure side. More than leakage into the outer compression chamber.
外側圧縮室の吸入容積が内側圧縮室の吸入容積よりも大きい非対称スクロール圧縮機では、吸入容積の小さい内側圧縮室の方がその吸入容積差によってクランク回転角に対する圧力上昇速度が大きい特徴を有する。一方、外側および内側圧縮室のいずれにおいても各圧縮室閉じ込み完了時から旋回スクロールが一回転した時点において次の圧縮室を形成することは、対称スクロールと同様である。 In an asymmetric scroll compressor in which the suction volume of the outer compression chamber is larger than the suction volume of the inner compression chamber, the inner compression chamber having a smaller suction volume has a feature that the pressure increase rate with respect to the crank rotation angle is larger due to the suction volume difference. On the other hand, in both the outer and inner compression chambers, the formation of the next compression chamber at the time when the orbiting scroll makes one revolution from the completion of closing of each compression chamber is the same as in the symmetric scroll.
以上の説明をさらに、図面を用いて説明する。図１８および図１９において、第２の圧縮室１５ｂ−１とその後に形成された第２の圧縮室１５ｂ−２を仕切る渦巻きラップ側面隙間Ｄ２、第１の圧縮室１５ａ−１とその後に形成される第１の圧縮室１５ａ−２を仕切
る渦巻きラップ側面隙間Ｄ１が存在する。図１９において、第１の圧縮室１５ａと第２の圧縮室１５ｂの圧力上昇速度を比較した場合、吸入容積の小さい第２圧縮室１５ｂの方が圧力変化が大きくなる。よって、第２の圧縮室１５ｂ間を仕切る渦巻きラップ側面隙間Ｄ２では、第１の圧縮室１５ｂ間を仕切る渦巻きラップ側面隙間Ｄ１よりも漏れが発生しやすくなる。渦巻きラップ側面を介した漏れは冷媒の再圧縮を引き起こすため、結果として無駄な仕事による圧縮性能低下を生じていた。
The above description will be further described with reference to the drawings. 18 and 19, the spiral wrap side surface gap D2 that partitions the second compression chamber 15b-1 and the second compression chamber 15b-2 formed thereafter, the first compression chamber 15a-1, and the subsequent compression chamber 15b-1. There is a spiral wrap side surface gap D1 that partitions the first compression chamber 15a-2. In FIG. 19, when the pressure increase speeds of the first compression chamber 15a and the second compression chamber 15b are compared, the pressure change is larger in the second compression chamber 15b having a smaller suction volume. Therefore, the spiral wrap side surface gap D2 that partitions the second compression chambers 15b is more likely to leak than the spiral wrap side surface gap D1 that partitions the first compression chambers 15b. Leakage through the spiral wrap side surface causes recompression of the refrigerant, resulting in a decrease in compression performance due to useless work.
本発明は、前記従来の課題を解決するもので、非対称スクロール圧縮機の圧縮室圧力分布と漏れ経路を考慮した給油経路と給油量制御により、圧縮機効率の向上を実現するスクロール圧縮機を提供することを目的とする。 The present invention solves the above-mentioned conventional problems, and provides a scroll compressor that realizes an improvement in compressor efficiency by an oil supply path and an oil supply amount control in consideration of a compression chamber pressure distribution and a leakage path of an asymmetric scroll compressor. The purpose is to do.
上記課題を解決するために、本発明のスクロール圧縮機は、鏡板から渦巻き状のラップが立ち上がる固定スクロール、及び旋回スクロールを噛み合わせて双方間に圧縮室を備え、圧縮室は旋回スクロールのラップ外側に形成される外側圧縮室と旋回スクロールの内側に形成される内側圧縮室を有し、外側圧縮室の吸入容積が内側圧縮室の吸入容積より大きく、旋回スクロールの背面には高圧領域と背圧室を形成し、旋回スクロールが円軌道に沿って所定の旋回半径で旋回することで、圧縮室が容積を変えながら中心に向かって移動し、固定スクロールに形成された吸入口から作動流体を吸入し、圧縮室に閉じ込めた後、圧縮、吐出の一連の動作を行うスクロール圧縮機であって、高圧領域と背圧室を結ぶ第１の経路と、背圧室と吸入口に連通しない圧縮室を結ぶ第２の経路を設け、第２の経路の圧縮室側開口端が、外側圧縮室と、内側圧縮室に間欠的に開口し、内側圧縮室への総給油量が外側圧縮室への総給油量より多くするものである。 In order to solve the above-described problems, a scroll compressor according to the present invention includes a fixed scroll in which a spiral wrap rises from an end plate and a revolving scroll, and a compression chamber is provided between the both. And the inner compression chamber formed inside the orbiting scroll. The suction volume of the outer compression chamber is larger than the suction volume of the inner compression chamber. A chamber is formed, and the orbiting scroll revolves with a predetermined orbiting radius along a circular orbit, so that the compression chamber moves toward the center while changing the volume, and sucks the working fluid from the suction port formed in the fixed scroll. The scroll compressor performs a series of operations of compression and discharge after being confined in the compression chamber, and communicates with the first path connecting the high pressure region and the back pressure chamber, and the back pressure chamber and the suction port. A second path connecting the compression chambers not provided, the compression chamber side opening end of the second path intermittently opens to the outer compression chamber and the inner compression chamber, and the total amount of oil supplied to the inner compression chamber is compressed outside Increase the total amount of oil supplied to the room.
本発明のスクロール圧縮機は、吸入口に連通しない内側圧縮室、および外側圧縮室へオイルを給油しつつ、外側圧縮室への総給油量より内側圧縮室への総給油量を多くすることにより、同じ圧縮室間における渦巻き状のラップ側面隙間からの作動流体の漏れを効果的に抑制でき、圧縮効率を向上できる。同時に、これらの圧縮室へ間欠的に給油を行うことで、給油量を絞る方向へ給油量制御の幅を広げることができ、給油量過多による粘性損失の増大を抑制できるため、高効率なスクロール圧縮機を提供できる。 The scroll compressor according to the present invention increases the total oil supply amount to the inner compression chamber from the total oil supply amount to the outer compression chamber while supplying oil to the inner compression chamber and the outer compression chamber that do not communicate with the suction port. The leakage of the working fluid from the spiral wrap side surface gap between the same compression chambers can be effectively suppressed, and the compression efficiency can be improved. At the same time, by intermittently supplying oil to these compression chambers, it is possible to widen the range of oil supply control in the direction of reducing the amount of oil supply, and it is possible to suppress an increase in viscosity loss due to excessive oil supply, so highly efficient scrolling A compressor can be provided.
第１の発明は、鏡板から渦巻き状のラップが立ち上がる固定スクロール、及び旋回スクロールを噛み合わせて双方間に圧縮室を備え、圧縮室は旋回スクロールのラップ外側に形成される外側圧縮室と旋回スクロールの内側に形成される内側圧縮室を有し、外側圧縮室の吸入容積が内側圧縮室の吸入容積より大きく、旋回スクロールの背面には高圧領域と背圧室を形成し、旋回スクロールが円軌道に沿って所定の旋回半径で旋回することで、圧縮室が容積を変えながら中心に向かって移動し、固定スクロールに形成された吸入口から作動流体を吸入し、圧縮室に閉じ込めた後、圧縮、吐出の一連の動作を行うスクロール圧縮機であって、高圧領域と背圧室を結ぶ第１の経路と、背圧室と吸入口に連通しない圧縮室を結ぶ第２の経路を設け、第２の経路の圧縮室側開口端が、外側圧縮室と、内側圧縮室に間欠的に開口し、内側圧縮室への総給油量が外側圧縮室への総給油量より多くするものである。この構成によれば、内側圧縮室においても、外側圧縮室においても、ひとつ前に作動流体を閉じ込んだ圧縮室と次に作動流体を閉じ込んだ圧縮室間の、渦巻き状のラップ側面隙間からの作動流体の漏れを効果的に抑制でき、かつ給油量過多による粘性損失の増大を抑制できる。 According to a first aspect of the present invention, there is provided a fixed scroll in which a spiral wrap rises from an end plate and a revolving scroll, and a compression chamber is provided between the two, and the compression chamber is formed on the outer side of the revolving scroll wrap and the revolving scroll. The inner compression chamber is formed inside, the suction volume of the outer compression chamber is larger than the suction volume of the inner compression chamber, a high pressure region and a back pressure chamber are formed on the back of the orbiting scroll, and the orbiting scroll is a circular orbit. , The compression chamber moves toward the center while changing the volume, sucks the working fluid from the suction port formed in the fixed scroll, confines it in the compression chamber, and then compresses it. A scroll compressor that performs a series of discharge operations, and includes a first path connecting the high pressure region and the back pressure chamber, and a second path connecting the back pressure chamber and the compression chamber not communicating with the suction port, 2 The compression chamber side opening end of the path, the outer compression chamber intermittently opened inside the compression chamber, in which the total amount of oil to the inner compression chamber is more than the total amount of oil to the outer compression chambers. According to this configuration, in both the inner compression chamber and the outer compression chamber, the spiral wrap side surface gap between the compression chamber that previously closed the working fluid and the compression chamber that next closed the working fluid. The leakage of the working fluid can be effectively suppressed, and an increase in viscosity loss due to excessive oil supply can be suppressed.
第２の発明は、特に第１の発明のスクロール圧縮機において、第２の経路の圧縮室側開口端を旋回スクロールのラップ上面に設け、開口端が、旋回スクロールの旋回運動に伴い
、固定スクロールのラップ鏡板面に設けた凹部に、間欠的に開口するものである。この構成によれば、第２の経路の径や長さや、凹部の形状によって、オイル供給量を連通時間で制御できるため、圧縮室内へのオイル供給量の調整範囲や、背圧室の圧力調整範囲が広がり、圧縮機の効率と背圧の安定性を更に向上できる。
According to a second aspect of the present invention, in the scroll compressor of the first aspect of the invention, the compression chamber side opening end of the second path is provided on the upper surface of the orbiting scroll wrap, and the opening end is fixed scroll in accordance with the orbiting scroll orbiting motion. It opens intermittently in a recess provided on the surface of the lap end plate. According to this configuration, since the oil supply amount can be controlled by the communication time depending on the diameter and length of the second path and the shape of the recess, the adjustment range of the oil supply amount into the compression chamber and the pressure adjustment of the back pressure chamber The range is expanded and the compressor efficiency and back pressure stability can be further improved.
第３の発明は、特に第１の発明のスクロール圧縮機において、第２の経路の圧縮室側開口端を旋回スクロールのラップ鏡板面に複数設け、旋回スクロールの旋回運動に伴い、開口端が、圧縮室と固定スクロールのラップ上面、及び圧縮室と固定スクロールのスラスト面を周期的に移動することで、前記圧縮室に間欠的に開口するものである。この構成によれば、発明２の効果に加えて、鏡板への孔加工のみで第２の経路が形成できるため、加工工数が低減できる。 According to a third aspect of the invention, in the scroll compressor of the first aspect of the invention, in particular, a plurality of compression chamber side opening ends of the second path are provided on the wrap end plate surface of the orbiting scroll. By periodically moving the upper surface of the compression chamber and the wrap of the fixed scroll and the thrust surface of the compression chamber and the fixed scroll, the compression chamber is intermittently opened. According to this configuration, in addition to the effect of the second aspect, the second path can be formed only by drilling the end plate, so that the number of processing steps can be reduced.
第４の発明は、特に第１から第３のいずれか１つの発明のスクロール圧縮機において、第１の経路の背圧室側開口端が、旋回スクロールの背面に設けられた高圧領域と背圧室を仕切るシール部材を往来するものである。この構成によれば、圧縮室への給油量を更に絞ることが出来るため、圧縮室内へのオイル供給量の調整範囲や、背圧室の圧力調整範囲がより広がり、圧縮機の効率と背圧の安定性を更に向上できる。また、第２の経路が背圧室と圧縮室を連通しない場合がクランク軸１回転中に存在しても、第１の経路を間欠的に連通させることで、過剰な背圧上昇を抑制できる。さらに、高圧領域から背圧室へ流入するオイル量を連通時間で制御できるため、第１の経路に油量調節のための絞り部を設ける必要がなくなり、絞り部に異物が噛み込むトラブルを回避でき、信頼性も向上できる。 In a fourth aspect of the invention, in particular, in the scroll compressor according to any one of the first to third aspects of the invention, the back pressure chamber side opening end of the first path is provided with a high pressure region and a back pressure provided on the back of the orbiting scroll. A seal member for partitioning the chamber is passed. According to this configuration, since the amount of oil supplied to the compression chamber can be further reduced, the adjustment range of the oil supply amount to the compression chamber and the pressure adjustment range of the back pressure chamber are further expanded, and the efficiency and back pressure of the compressor are increased. Can be further improved. Further, even if the second path does not communicate with the back pressure chamber and the compression chamber, even if the crankshaft is rotating once, excessive back pressure rise can be suppressed by intermittently communicating the first path. . Furthermore, since the amount of oil flowing from the high pressure region into the back pressure chamber can be controlled by the communication time, there is no need to provide a throttle for adjusting the amount of oil in the first path, and the trouble of foreign matter getting caught in the throttle is avoided. And reliability can be improved.
第５の発明は、特に第１から第４のいずれか１つに記載のスクロール圧縮機において、背圧室と吸入口に連通する圧縮室を結ぶ第３の経路を設けたものである。この構成によれば、背圧室から供給されるオイルが、吸入に連通する圧縮室のシールの役割を果たし、吸入行程における作動流体の漏れを抑制でき、体積効率を向上でき、圧縮機の効率をさらに向上できる。 According to a fifth aspect of the invention, in particular, in the scroll compressor according to any one of the first to fourth aspects, a third path connecting the back pressure chamber and the compression chamber communicating with the suction port is provided. According to this configuration, the oil supplied from the back pressure chamber serves as a seal for the compression chamber communicating with the suction, can suppress the leakage of the working fluid in the suction stroke, can improve the volumetric efficiency, and the compressor efficiency Can be further improved.
第６の発明は、特に第１から第４のいずれか１つに記載のスクロール圧縮機において、高圧領域と吸入口に連通する圧縮室を結ぶ第４の経路を設けたものである。この構成によれば、高圧のオイルが吸入に連通する圧縮室に供給されるため、差圧の大きい高負荷運転時の潤滑性能が向上し、ラップの異常磨耗が抑制でき、信頼性を向上できる。 According to a sixth aspect of the present invention, in the scroll compressor according to any one of the first to fourth aspects, a fourth path is provided to connect the high pressure region and the compression chamber communicating with the suction port. According to this configuration, since high-pressure oil is supplied to the compression chamber that communicates with suction, the lubrication performance during high-load operation with a large differential pressure can be improved, abnormal wear of the lap can be suppressed, and reliability can be improved. .
第７の発明は、特に第５から第６のいずれか１つに記載のスクロール圧縮機において、第３、及び第４の経路の圧縮室側開口端を、旋回スクロールのラップ上面に設けたものである。この構成によれば、給油経路の開閉によるウォーターハンマ現象が発生せず、作動流体に起因する騒音を低減できる。 A seventh aspect of the present invention is the scroll compressor according to any one of the fifth to sixth aspects, wherein the compression chamber side opening ends of the third and fourth paths are provided on the upper surface of the orbiting scroll wrap. It is. According to this configuration, the water hammer phenomenon due to opening and closing of the oil supply path does not occur, and noise caused by the working fluid can be reduced.
第８の発明は、特に第５または第６に記載のスクロール圧縮機において、第３、及び第４の経路の圧縮室側開口端を前記旋回スクロールのラップ上面に設け、開口端が、旋回スクロールの旋回運動に伴い、固定スクロールのラップ鏡板面に設けた凹部に、間欠的に開口するものである。この構成によれば、第３、および第４の経路の径や長さや、凹部の形状によって、オイル供給量を連通時間で制御できるため、圧縮室内へのオイル供給量の調整範囲が広がり、吸入加熱による体積効率の悪化を抑制でき、圧縮機の効率を向上できる。 According to an eighth aspect of the present invention, in the scroll compressor according to the fifth or sixth aspect, the compression chamber side opening ends of the third and fourth paths are provided on the wrap upper surface of the orbiting scroll, and the opening end is the orbiting scroll. As a result of the swiveling motion, the opening is intermittently opened in a recess provided on the lap end plate surface of the fixed scroll. According to this configuration, the oil supply amount can be controlled by the communication time depending on the diameters and lengths of the third and fourth paths and the shape of the recesses. Deterioration of volumetric efficiency due to heating can be suppressed and the efficiency of the compressor can be improved.
第９の発明は、特に第５または第６に記載のスクロール圧縮機において、第３、及び第４の経路の圧縮室側開口端を旋回スクロールのラップ鏡板面に複数設け、旋回スクロールの旋回運動に伴い、開口端が、圧縮室と固定スクロールのラップ上面、及び圧縮室と固定スクロールのスラスト面を周期的に移動することで、圧縮室に間欠的に開口するものであ
る。この構成によれば、発明８の効果に加えて、鏡板への孔加工のみで第３、および第４の経路が形成できるため、加工工数が低減できる。
According to a ninth aspect of the present invention, in the scroll compressor according to the fifth or sixth aspect, a plurality of compression chamber side opening ends of the third and fourth paths are provided on the lap end plate surface of the orbiting scroll, and the orbiting scroll is revolving. Accordingly, the opening end periodically opens in the compression chamber by periodically moving on the wrap upper surface of the compression chamber and the fixed scroll and the thrust surface of the compression chamber and the fixed scroll. According to this configuration, in addition to the effect of the eighth aspect, the third and fourth paths can be formed only by drilling the end plate, so that the number of processing steps can be reduced.
第１０の発明は、特に第１から第９のいずれか１つに記載のスクロール圧縮機において、作動流体を高圧流体、例えば二酸化炭素とするものである。この構成によれば、作動流体の作動圧力が高い場合においても、圧縮室間の渦巻き状のラップ側面隙間からの作動流体の漏れの漏れを効果的に抑制しつつ、安定した背圧を印加することができる。 According to a tenth aspect of the invention, in particular, in the scroll compressor according to any one of the first to ninth aspects, the working fluid is a high-pressure fluid, for example, carbon dioxide. According to this configuration, even when the working pressure of the working fluid is high, a stable back pressure is applied while effectively suppressing leakage of the working fluid from the spiral wrap side surface gap between the compression chambers. be able to.
以下、本発明の実施の形態について、図面を参照しながら説明する。なお、この実施の形態によって本発明が限定されるものではない。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.
（実施の形態１）
図１は、本発明の第１の実施の形態に係るスクロール圧縮機の縦断面図である。図２と図３は、図１の圧縮機構部の要部拡大断面図であり、図２は内連通を示し、図３は外連通を示す。
(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a scroll compressor according to the first embodiment of the present invention. 2 and 3 are enlarged cross-sectional views of the main part of the compression mechanism of FIG. 1, FIG. 2 shows internal communication, and FIG. 3 shows external communication.
以下、本実施の形態１のスクロール圧縮機について、その構成、動作、作用を説明する。 Hereinafter, the configuration, operation, and action of the scroll compressor according to the first embodiment will be described.
図１に示すように本発明のスクロール圧縮機は、密閉容器１と、その内部に圧縮機構２、モータ部３、貯油部２０を備えて構成されている。図２と図３を用いて圧縮機構部の詳細を説明すると、密閉容器１内に溶接や焼き嵌めなどして固定したシャフト４の主軸受部材１１と、この主軸受部材１１上にボルト止めした固定スクロール１２との間に、固定スクロール１２と噛み合う旋回スクロール１３を挟み込んでスクロール式の圧縮機構２を構成している。旋回スクロール１３と主軸受部材１１との間には、旋回スクロール１３の自転を防止して円軌道運動するように案内するオルダムリングなどによる自転拘束機構１４を設け、シャフト４の上端にある偏心軸部４ａにて旋回スクロール１３を偏心駆動することにより、旋回スクロール１３を円軌道運動させる。これにより固定スクロール１２と旋回スクロール１３との間に形成している圧縮室１５が、外周側から中央部に向かって容積を縮めながら移動することを利用して、密閉容器１外に通じた吸入パイプ１６及び固定スクロール１２の外周部の吸入口１７から作動流体を吸入して、圧縮室１５に閉じ込んだのち圧縮を行う。所定の圧力に到達した作動流体は、固定スクロール１２の中央部の吐出口１８からリード弁１９を押し開いて、密閉容器１内に吐出される。 As shown in FIG. 1, the scroll compressor of the present invention is configured to include a hermetic container 1 and a compression mechanism 2, a motor unit 3, and an oil storage unit 20 therein. The details of the compression mechanism will be described with reference to FIGS. 2 and 3. The main bearing member 11 of the shaft 4 fixed by welding or shrink fitting in the sealed container 1, and bolted on the main bearing member 11. A scroll-type compression mechanism 2 is configured by sandwiching a turning scroll 13 meshing with the fixed scroll 12 between the fixed scroll 12. Between the orbiting scroll 13 and the main bearing member 11, there is provided a rotation restraining mechanism 14 such as an Oldham ring that guides the orbiting scroll 13 so as to prevent the rotation of the orbiting scroll and move in a circular orbit, and an eccentric shaft at the upper end of the shaft 4. The orbiting scroll 13 is moved in a circular orbit by driving the orbiting scroll 13 eccentrically by the portion 4a. By using the fact that the compression chamber 15 formed between the fixed scroll 12 and the orbiting scroll 13 moves while shrinking the volume from the outer peripheral side toward the center portion, the suction communicated outside the sealed container 1. The working fluid is sucked from the suction port 17 in the outer peripheral portion of the pipe 16 and the fixed scroll 12 and is compressed in the compression chamber 15 after being closed. The working fluid that has reached a predetermined pressure pushes the reed valve 19 through the discharge port 18 at the center of the fixed scroll 12 and is discharged into the sealed container 1.
またシャフト４の一端にはポンプ２５が設けられ、ポンプ２５の吸い込み口が貯油部２０内に存在するように配置する。ポンプ２５はスクロール圧縮機と同時に駆動されるため、ポンプ２５は密閉容器１の底部に設けられた貯油部２０にあるオイル６を、圧力条件や運転速度に関係なく、確実に吸い上げることができ、オイル切れの心配も解消される。ポンプ２５で吸い上げたオイル６は、シャフト４内を通縦しているオイル供給穴２６を通じて圧縮機構２に供給される。なお、オイル６をポンプ２５で吸い上げる前、もしくは吸い上げた後に、オイルフィルタ等でオイル６から異物を除去すると、圧縮機構２への異物混入が防止でき、更なる信頼性向上を図ることができる。 Further, a pump 25 is provided at one end of the shaft 4, and the suction port of the pump 25 is disposed in the oil storage unit 20. Since the pump 25 is driven simultaneously with the scroll compressor, the pump 25 can reliably suck up the oil 6 in the oil storage unit 20 provided at the bottom of the hermetic container 1 regardless of the pressure condition and the operation speed. The worry of running out of oil is also eliminated. The oil 6 sucked up by the pump 25 is supplied to the compression mechanism 2 through an oil supply hole 26 running vertically through the shaft 4. If foreign matter is removed from the oil 6 with an oil filter or the like before or after the oil 25 is sucked up by the pump 25, foreign matter can be prevented from entering the compression mechanism 2 and further reliability can be improved.
圧縮機構２に導かれたオイル６は、スクロール圧縮機の吐出圧力とほぼ同等であり、旋回スクロール１３に対する背圧源ともなる。これにより、旋回スクロール１３は固定スクロール１２から離れたり片当たり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。さらにオイル６の一部は、供給圧や自重によって、逃げ場を求めるようにして偏心軸部４ａと旋回スクロール１３との嵌合部、シャフト４と主軸受部材１１との間の軸受部６６に進入してそれぞれの部分を潤滑した後落下し、貯油部２０へ戻る。 The oil 6 guided to the compression mechanism 2 is substantially equal to the discharge pressure of the scroll compressor and also serves as a back pressure source for the orbiting scroll 13. As a result, the orbiting scroll 13 does not move away from the fixed scroll 12 and does not come into contact with one another, and the predetermined compression function is stably exhibited. Further, a part of the oil 6 enters the bearing portion 66 between the shaft 4 and the main bearing member 11, the fitting portion between the eccentric shaft portion 4 a and the orbiting scroll 13 so as to obtain a clearance by the supply pressure and the own weight. Then, the respective parts are lubricated and then dropped and returned to the oil storage unit 20.
固定スクロール１２と旋回スクロール１３により形成される圧縮室１５には、旋回スクロール１３のラップ外壁側に形成される外側圧縮室１５ａと、ラップ内壁側に形成される内側圧縮室１５ｂがあり、外側圧縮室１５ａの吸入容積の方が、内側圧縮室１５ｂの吸入容積より大きい。このことにより、図１９に示したように、クランク回転角に対する内側圧縮室１５ｂの圧力上昇速度は外側圧縮室１５ａの圧力上昇速度よりも速くなり、結果として、図１８に示した渦巻きラップ側面Ｄ２で仕切られる内側圧縮室１５ｂ−１と低圧側に形成される内側圧縮室１５ｂ−２の圧力差が大きくなることから、外側圧縮室１５ａと比較し内側圧縮室１５ｂの渦巻きラップ側面Ｄ２を介して作動流体が漏れやすいことになる。 The compression chamber 15 formed by the fixed scroll 12 and the orbiting scroll 13 includes an outer compression chamber 15a formed on the wrap outer wall side of the orbiting scroll 13 and an inner compression chamber 15b formed on the wrap inner wall side. The suction volume of the chamber 15a is larger than the suction volume of the inner compression chamber 15b. As a result, as shown in FIG. 19, the pressure increase rate of the inner compression chamber 15b with respect to the crank rotation angle becomes faster than the pressure increase rate of the outer compression chamber 15a. As a result, the spiral wrap side surface D2 shown in FIG. Since the pressure difference between the inner compression chamber 15b-1 partitioned by the inner compression chamber 15b-2 formed on the low pressure side and the inner compression chamber 15b-2 is larger than that of the outer compression chamber 15a, the spiral compression wrap side surface D2 of the inner compression chamber 15b is used. The working fluid is likely to leak.
そこで、本実施の形態のスクロール圧縮機では、貯油部２０から内側圧縮室１５ｂに導く給油量制御経路５５を第１の経路５５−１と第２の経路５５−２で構成し、内側圧縮室連通凹部８４の断面積を外側圧縮室連通凹部８５の断面積より大きく設定することによって、圧力上昇速度の大きい外側圧縮室１５ｂへ積極的にオイル供給することで、１つ前に形成された内側圧縮室１５ｂ−１から、次に形成された内側圧縮室１５ｂ−２への作動流体の漏れを抑制することができる。 Therefore, in the scroll compressor of the present embodiment, the oil supply amount control path 55 that leads from the oil storage unit 20 to the inner compression chamber 15b is configured by the first path 55-1 and the second path 55-2, and the inner compression chamber. By setting the cross-sectional area of the communication recess 84 to be larger than the cross-sectional area of the outer compression chamber communication recess 85, the oil is positively supplied to the outer compression chamber 15b having a high pressure increase rate, thereby forming the inner side formed immediately before. The leakage of the working fluid from the compression chamber 15b-1 to the inner compression chamber 15b-2 formed next can be suppressed.
オイル供給穴２６から流出したオイル６は、第１の経路５５−１の高圧領域側開口端５５−１ａから第１の経路５５−１に流入し、第１の経路５５−１の背圧室側開口端５５−１ｂから流出する。また、高圧領域３０と背圧室２９は、シール部材７８によって密接に区画されているため、高圧領域３０と背圧室２９の間のオイル６の漏れ出しは無い。 The oil 6 flowing out from the oil supply hole 26 flows into the first path 55-1 from the high-pressure region side opening end 55-1 a of the first path 55-1, and the back pressure chamber of the first path 55-1. It flows out from the side opening end 55-1b. Further, since the high pressure region 30 and the back pressure chamber 29 are closely separated by the seal member 78, the oil 6 does not leak between the high pressure region 30 and the back pressure chamber 29.
図２に示すクランク角（図４（Ａ）のクランク角）においては、第１の経路５５−１の背圧室側開口端５５−１ｂが高圧領域３０に開口している。よって、第１の経路５５−１の高圧領域側開口端５５−１ａと背圧室側開口端５５−１ｂの圧力差がなくなるので、第１の経路５５−１内でのオイル６の移動はない。 At the crank angle shown in FIG. 2 (the crank angle in FIG. 4A), the back pressure chamber side opening end 55-1b of the first path 55-1 is open to the high pressure region 30. Therefore, since there is no pressure difference between the high pressure region side opening end 55-1a and the back pressure chamber side opening end 55-1b of the first path 55-1, the movement of the oil 6 in the first path 55-1 is Absent.
対して、図３に示すクランク角（図４（Ｂ）、（Ｃ）、（Ｄ）のクランク角）においては、第１の経路５５−１の背圧室側開口端５５−１ｂがシール部材７８を跨いで背圧室２９に開口している。よって、高圧室３０より圧力の低い（＝背圧室２９は、高圧と吸入圧の中間の圧力に保たれている）背圧室２９に圧力差によってオイル６が流出される。 On the other hand, at the crank angle shown in FIG. 3 (the crank angles in FIGS. 4B, 4C, and 4D), the back pressure chamber side opening end 55-1b of the first path 55-1 is the seal member. The back pressure chamber 29 is opened across 78. Therefore, the oil 6 flows out into the back pressure chamber 29 having a pressure lower than that of the high pressure chamber 30 (= the back pressure chamber 29 is maintained at an intermediate pressure between the high pressure and the suction pressure) due to the pressure difference.
すなわち、クランク角によって、第１の経路５５−１の背圧室側開口端５５−１ｂが、シール部材７８を往来することにより、高圧領域３０と背圧室２９の非連通状態と連通状態を繰り返す。よって、背圧室２９、ひいては内側圧縮室１５ｂへのオイル６の給油量を絞ることが出来るため、内側圧縮室１５ｂ内へのオイル供給量の調整範囲を広げることが可能となるため、内側圧縮室１５ｂ内への過剰なオイル６の供給による粘性損失の増大を抑制でき、圧縮機の効率を向上できる。また、背圧室２９に流入するオイル６の調整範囲も広がり、背圧を下げることが出来るため、旋回スクロール１３の固定スクロール１２への押付力を緩和でき、旋回スクロール１３のスラスト面１３ｄや旋回スクロール１３のラップ先端１３ｃでの摺動損失を緩和でき、圧縮機の効率を向上できる。また、第２の経路５５−２が背圧室２９と内側圧縮室１５ｂを連通しない場合がクランク軸１回転中に存在しても、第１の経路５５−１を間欠的に連通させることで、過剰な背圧上昇を抑制でき、圧縮機構２の信頼性が向上できる。さらに、高圧領域３０から背圧室２９へ流入するオイル量を連通時間で制御できるため、第１の経路５５−１に油量調節のための絞り部を設ける必要がなくなり、絞り部に異物が噛み込むトラブルを回避でき、圧縮機構２の信頼性が向上できる。 That is, the back pressure chamber side opening end 55-1b of the first path 55-1 travels through the seal member 78 depending on the crank angle, so that the non-communication state and the communication state of the high pressure region 30 and the back pressure chamber 29 are changed. repeat. Therefore, since the amount of oil 6 supplied to the back pressure chamber 29 and thus to the inner compression chamber 15b can be reduced, the adjustment range of the oil supply amount to the inner compression chamber 15b can be widened. An increase in viscosity loss due to the excessive supply of oil 6 into the chamber 15b can be suppressed, and the efficiency of the compressor can be improved. In addition, since the adjustment range of the oil 6 flowing into the back pressure chamber 29 is widened and the back pressure can be reduced, the pressing force of the orbiting scroll 13 against the fixed scroll 12 can be reduced, and the thrust surface 13d of the orbiting scroll 13 and the orbiting can be reduced. The sliding loss at the wrap tip 13c of the scroll 13 can be alleviated, and the efficiency of the compressor can be improved. Further, even when the second path 55-2 does not communicate with the back pressure chamber 29 and the inner compression chamber 15b during the one rotation of the crankshaft, the first path 55-1 is intermittently communicated. Thus, an excessive increase in back pressure can be suppressed, and the reliability of the compression mechanism 2 can be improved. Further, since the amount of oil flowing from the high pressure region 30 into the back pressure chamber 29 can be controlled by the communication time, it is not necessary to provide a throttle portion for adjusting the oil amount in the first path 55-1 and foreign matter is present in the throttle portion. The trouble of biting can be avoided and the reliability of the compression mechanism 2 can be improved.
次に、背圧室２９に流入したオイル６は、第２の経路５５−２の背圧室側開口端５５−２ａから第２の経路５５−２を経て第２の経路５５−２の圧縮室側開口端５５−２ｂに至
る。さらに、固定スクロール１２に設けられた内側圧縮室連通凹部８４と外側圧縮室連通凹部８５を経て、内側圧縮室１５ｂと外側圧縮室１５ａに振り分けられて流入する。
Next, the oil 6 flowing into the back pressure chamber 29 is compressed in the second path 55-2 from the back pressure chamber side opening end 55-2a of the second path 55-2 through the second path 55-2. It reaches the chamber side opening end 55-2b. Further, the air flows through the inner compression chamber communication recess 84 and the outer compression chamber communication recess 85 provided in the fixed scroll 12 and flows into the inner compression chamber 15b and the outer compression chamber 15a.
図２に示すクランク角（図５（Ｃ）のクランク角）においては、第２の経路５５−２の圧縮室側開口端５５−２ｂが内側圧縮室連通凹部８４と連通状態であり、内側圧縮室１５ｂにオイル６が供給されている。 At the crank angle shown in FIG. 2 (the crank angle in FIG. 5C), the compression chamber side opening end 55-2b of the second path 55-2 is in communication with the inner compression chamber communication recess 84, and the inner compression is performed. Oil 6 is supplied to the chamber 15b.
対して、図３に示すクランク角（図５（Ａ）のクランク角）においては、第２の経路５５−２の圧縮室側開口端５５−２ｂが外側圧縮室連通凹部８５と連通状態にあり、外側圧縮室１５ａにオイル６が供給されている。 On the other hand, at the crank angle shown in FIG. 3 (the crank angle in FIG. 5A), the compression chamber side opening end 55-2b of the second path 55-2 is in communication with the outer compression chamber communication recess 85. The oil 6 is supplied to the outer compression chamber 15a.
内側圧縮室連通凹部８４の断面積は、外側圧縮室連通凹部８５の断面積より大きいため、旋回スクロール１３の旋回に伴う、第２の経路５５−２の圧縮室側開口端５５−２ｂと内側圧縮室連通凹部８４の開口時間は、外側圧縮室連通凹部８５との開口時間より長くなる。よって、内側圧縮室１５ｂへの給油量が外側圧縮室１５ａへの給油量より多くなり、圧力上昇速度の大きい外側圧縮室１５ｂへ積極的にオイルが供給でき、１つ前に形成された内側圧縮室１５ｂ−１から、次に形成された内側圧縮室１５ｂ−２への作動流体の漏れを抑制することができる。 Since the cross-sectional area of the inner compression chamber communication recess 84 is larger than the cross-sectional area of the outer compression chamber communication recess 85, the compression chamber side opening end 55-2b and the inner side of the second path 55-2 accompanying the turning of the orbiting scroll 13 are included. The opening time of the compression chamber communication recess 84 is longer than the opening time of the outer compression chamber communication recess 85. Therefore, the amount of oil supplied to the inner compression chamber 15b is larger than the amount of oil supplied to the outer compression chamber 15a, and oil can be positively supplied to the outer compression chamber 15b having a large pressure increase rate. The leakage of the working fluid from the chamber 15b-1 to the inner compression chamber 15b-2 formed next can be suppressed.
よって、内側圧縮室１５ｂにおいても、外側圧縮室１５ａにおいても、ひとつ前に作動流体を閉じ込んだ圧縮室１５と次に作動流体を閉じ込んだ圧縮室１５間の、渦巻き状のラップ側面隙間Ｄ２からの作動流体の漏れを効果的に抑制でき、再圧縮による圧縮効率の低下を抑制できる。 Therefore, in both the inner compression chamber 15b and the outer compression chamber 15a, the spiral wrap side surface gap D2 between the compression chamber 15 that previously closed the working fluid and the compression chamber 15 that next closed the working fluid. It is possible to effectively suppress the leakage of the working fluid from the cylinder, and to suppress a decrease in compression efficiency due to recompression.
高圧領域３０から背圧室２９への給油量は、第１の経路５５−１の背圧室側開口端５５−１ｂの断面積や開口位置を変化させて制御可能であるし、背圧室２９から内側圧縮室１５ｂ、および外側圧縮室１５ａへの給油量は、第２の経路５５−２の断面積や、第２の経路５５−２の圧縮室側開口端５５−２ｂの断面積を変化させて制御可能である。 The amount of oil supplied from the high pressure region 30 to the back pressure chamber 29 can be controlled by changing the cross-sectional area and the opening position of the back pressure chamber side opening end 55-1b of the first path 55-1, and the back pressure chamber. The amount of oil supply from 29 to the inner compression chamber 15b and the outer compression chamber 15a is the sectional area of the second path 55-2 and the sectional area of the compression chamber side opening end 55-2b of the second path 55-2. It can be controlled by changing.
また、図５（Ｂ）、（Ｄ）に示すクランク角では、第２の経路５５−２の圧縮室側開口端５５−２ｂは内側圧縮室連通凹部８４とも外側圧縮室連通凹部８５とも連通していないため、内側圧縮室１５ｂへも外側圧縮室１５ａへも給油されない。よって、給油量過多による粘性損失の増大を抑制できるため、圧縮機の効率を向上できる。 5B and 5D, the compression chamber side opening end 55-2b of the second path 55-2 communicates with the inner compression chamber communication recess 84 and the outer compression chamber communication recess 85. Therefore, neither the inner compression chamber 15b nor the outer compression chamber 15a is refueled. Therefore, an increase in viscosity loss due to excessive oil supply can be suppressed, and the efficiency of the compressor can be improved.
なお、内側圧縮室１５ｂと外側圧縮室１５ａの給油量の大小を、内側圧縮室連通凹部８４と外側圧縮室連通凹部８５の断面積の大小により制御していたが、内側圧縮室連通凹部８４と外側圧縮室連通凹部８５の深さや、位置を変化させて給油量の大小を制御しても良い。 The amount of oil supply in the inner compression chamber 15b and the outer compression chamber 15a is controlled by the size of the cross-sectional areas of the inner compression chamber communication recess 84 and the outer compression chamber communication recess 85. The amount of oil supply may be controlled by changing the depth and position of the outer compression chamber communication recess 85.
（実施の形態２）
図６と図７は、本発明の第２の実施の形態に係るスクロール圧縮機の圧縮機構部の拡大断面図である。なお、図６は内連通を示し、図７は外連通を示す。図６と図７において、圧縮室１５へのオイル供給について、第２の経路５５−２の圧縮室側開口端以外は前記実施の形態１と同様なので、図２と同じ構成要素については同じ符号を用い、第２の経路５５−２の圧縮室側開口端に関する説明のみを行い、他は省略する。
(Embodiment 2)
6 and 7 are enlarged cross-sectional views of the compression mechanism portion of the scroll compressor according to the second embodiment of the present invention. 6 shows internal communication, and FIG. 7 shows external communication. 6 and 7, the oil supply to the compression chamber 15 is the same as that of the first embodiment except for the compression chamber side opening end of the second path 55-2, and therefore the same components as those in FIG. Only the description about the compression chamber side opening end of the second path 55-2 will be given, and the others will be omitted.
図６に示すように、本実施の形態では、第２の経路５５−２の圧縮室側開口端が、内側圧縮室側開口端５５−２ｃと外側圧縮室側開口端５５−２ｄから構成されている。背圧室２９に流入したオイル６は、第２の経路５５−２の背圧室側開口端５５−２ａから第２の経路５５−２を経て第２の経路５５−２の内側圧縮室側開口端５５−２ｃと外側圧縮室側
開口端５５−２ｄに振り分けられる。
As shown in FIG. 6, in the present embodiment, the compression chamber side opening end of the second path 55-2 is constituted by an inner compression chamber side opening end 55-2c and an outer compression chamber side opening end 55-2d. ing. The oil 6 that has flowed into the back pressure chamber 29 passes through the second path 55-2 from the back pressure chamber side opening end 55-2a of the second path 55-2, and reaches the inner compression chamber side of the second path 55-2. It is distributed to the opening end 55-2c and the outer compression chamber side opening end 55-2d.
図６に示すクランク角（図８（Ｃ）のクランク角）においては、第２の経路５５−２の内側圧縮室側開口端５５−２ｃが内側圧縮室１５ｂと連通状態であり、内側圧縮室１５ｂにオイル６が供給されている。 At the crank angle shown in FIG. 6 (the crank angle in FIG. 8C), the inner compression chamber side opening end 55-2c of the second path 55-2 is in communication with the inner compression chamber 15b, and the inner compression chamber Oil 6 is supplied to 15b.
対して、図７示すクランク角（図８（Ａ）のクランク角）においては、第２の経路５５−２の外側圧縮室側開口端５５−２ｄが外側圧縮室１５ａと連通状態にあり、外側圧縮室１５ａにオイル６が供給されている。 On the other hand, at the crank angle shown in FIG. 7 (the crank angle in FIG. 8A), the outer compression chamber side opening end 55-2d of the second path 55-2 is in communication with the outer compression chamber 15a, and the outer side Oil 6 is supplied to the compression chamber 15a.
内側圧縮室側開口端５５−２ｃの断面積は、外側圧縮室側開口端５５−２ｄの断面積より大きいため、内側圧縮室１５ｂへの給油量が外側圧縮室１５ａへの給油量より多くなり、圧力上昇速度の大きい外側圧縮室１５ｂへ積極的にオイルが供給でき、１つ前に形成された内側圧縮室１５ｂ−１から、次に形成された内側圧縮室１５ｂ−２への作動流体の漏れを抑制することができる。 Since the sectional area of the inner compression chamber side opening end 55-2c is larger than the sectional area of the outer compression chamber side opening end 55-2d, the amount of oil supplied to the inner compression chamber 15b becomes larger than the amount of oil supplied to the outer compression chamber 15a. The oil can be positively supplied to the outer compression chamber 15b having a large pressure increase speed, and the working fluid can be transferred from the inner compression chamber 15b-1 formed one before to the inner compression chamber 15b-2 formed next. Leakage can be suppressed.
よって、内側圧縮室１５ｂにおいても、外側圧縮室１５ａにおいても、ひとつ前に作動流体を閉じ込んだ圧縮室１５と次に作動流体を閉じ込んだ圧縮室１５間の、渦巻き状のラップ側面隙間Ｄ２からの作動流体の漏れを効果的に抑制でき、再圧縮による圧縮効率の低下を抑制できる。 Therefore, in both the inner compression chamber 15b and the outer compression chamber 15a, the spiral wrap side surface gap D2 between the compression chamber 15 that previously closed the working fluid and the compression chamber 15 that next closed the working fluid. It is possible to effectively suppress the leakage of the working fluid from the cylinder, and to suppress a decrease in compression efficiency due to recompression.
背圧室２９から内側圧縮室１５ｂ、および外側圧縮室１５ａへの給油量は、第２の経路５５−２の断面積や、第２の経路５５−２の内側圧縮室側開口端５５−２ｃや外側圧縮室側開口端５５−２ｄの断面積を変化させて制御可能である。 The amount of oil supplied from the back pressure chamber 29 to the inner compression chamber 15b and the outer compression chamber 15a depends on the cross-sectional area of the second path 55-2 and the inner compression chamber side opening end 55-2c of the second path 55-2. Alternatively, it can be controlled by changing the cross-sectional area of the outer compression chamber side opening end 55-2d.
また、図８（Ｂ）、（Ｄ）に示すクランク角では、第２の経路５５−２の内側圧縮室側開口端５５−２ｃや外側圧縮室側開口端５５−２ｄが固定スクロール１２のラップ先端によって閉塞されているため、内側圧縮室１５ｂへも外側圧縮室１５ａへも連通していないので、内側圧縮室１５ｂへも外側圧縮室１５ａへも給油されない。よって、給油量過多による粘性損失の増大を抑制できるため、圧縮機の効率を向上できる。 8B and 8D, the inner compression chamber side opening end 55-2c and the outer compression chamber side opening end 55-2d of the second path 55-2 are wrapped with the fixed scroll 12. Since it is blocked by the tip, it does not communicate with the inner compression chamber 15b or the outer compression chamber 15a, so that neither the inner compression chamber 15b nor the outer compression chamber 15a is refueled. Therefore, an increase in viscosity loss due to excessive oil supply can be suppressed, and the efficiency of the compressor can be improved.
（実施の形態３）
図９と図１０は、本発明の第３の実施の形態に係るスクロール圧縮機の圧縮機構部の拡大断面図であり、図９は内連通を示し、図１０は外連通を示す。図９と図１０において、吸入室８６へのオイル供給について、第３の経路５５−３以外は前記実施の形態１と同様なので、図２と同じ構成要素については同じ符号を用い、第３の経路５５−３に関する説明のみを行い、他は省略する。
(Embodiment 3)
9 and 10 are enlarged cross-sectional views of the compression mechanism portion of the scroll compressor according to the third embodiment of the present invention. FIG. 9 shows internal communication and FIG. 10 shows external communication. 9 and 10, the oil supply to the suction chamber 86 is the same as that of the first embodiment except for the third path 55-3. Therefore, the same reference numerals are used for the same components as in FIG. Only the route 55-3 will be described, and the others will be omitted.
図９に示すように、本実施の形態では、第３の経路５５−３を設けている。第３の経路５５−３の一方の端は、背圧室側開口端５５−３ａであり、背圧室２９に常時臨んでいる。他方の端は吸入室側開口端５５−３ｂであり、旋回スクロール１３のラップ上面に設けられており、ザグリ８７を通じて常時吸入室８６に臨んでいる。 As shown in FIG. 9, in the present embodiment, a third path 55-3 is provided. One end of the third path 55-3 is a back pressure chamber side opening end 55-3 a and always faces the back pressure chamber 29. The other end is a suction chamber side opening end 55-3b, which is provided on the upper surface of the orbiting scroll 13 and faces the suction chamber 86 through a counterbore 87 at all times.
背圧室２９に流入したオイル６は、第３の経路５５−３の背圧室側開口端５５−３ａから第３の経路５５−３を経て、第３の経路５５−３の吸入室側開口端５５−３ｂから、ザグリ８７を経て吸入室８６に流入する。 The oil 6 that has flowed into the back pressure chamber 29 passes from the back pressure chamber side opening end 55-3a of the third path 55-3 through the third path 55-3, and then into the suction chamber side of the third path 55-3. It flows into the suction chamber 86 through the counterbore 87 from the open end 55-3b.
図９と図１０においても、すなわち図１１（Ａ）から（Ｄ）に示す全てのクランク角において、第３の経路５５−３の吸入室側開口端５５−３ｂは吸入室８６と常時連通状態であり、常時吸入室８６にオイル６が供給されている。よって、吸入室８６に常時オイル６
が供給されることにより、オイル６がシールの役割を果たし、吸入に連通する圧縮室（＝吸入室８６）の吸入行程における作動流体の漏れが低減でき、体積効率を向上できるため、圧縮機の効率向上が可能である。
Also in FIGS. 9 and 10, that is, at all crank angles shown in FIGS. 11A to 11D, the suction chamber side open end 55-3b of the third path 55-3 is always in communication with the suction chamber 86. The oil 6 is always supplied to the suction chamber 86. Therefore, the oil 6 is always in the suction chamber 86
Since the oil 6 serves as a seal and the leakage of the working fluid in the suction stroke of the compression chamber (= suction chamber 86) communicating with the suction can be reduced and the volumetric efficiency can be improved, Efficiency can be improved.
背圧室２９から吸入室８６への給油量は、第３の経路５５−３の断面積や、背圧室側開口端５５−３ａの断面積、吸入室側開口端５５−３ｂの断面積や開口位置、ザグリ８７の断面積や深さを変化させることで制御可能である。なお、ザグリ８７をなくしても良い。 The amount of oil supplied from the back pressure chamber 29 to the suction chamber 86 depends on the cross-sectional area of the third path 55-3, the cross-sectional area of the back pressure chamber-side opening end 55-3a, and the cross-sectional area of the suction chamber-side opening end 55-3b. Further, it can be controlled by changing the opening position and the cross-sectional area and depth of the counterbore 87. The counterbore 87 may be eliminated.
さらに、図１２および図１３に示すように、第３の経路の吸入室側開口端５５−３ｂを外側吸入室連通凹部８８−２と内側吸入室連通凹部８８−１を経て、吸入室８６に開口させる構成としても良い。この場合、吸入室側開口端５５−３ｂが、外側吸入室連通凹部８８−２か内側吸入室連通凹部８８−１に臨んでいるクランク角においてのみ外側吸入室８６−２もしくは内側吸入室８６−１にオイル６が給油されるので、間欠的な給油が可能となる。 Further, as shown in FIG. 12 and FIG. 13, the suction chamber side opening end 55-3b of the third path passes through the outer suction chamber communication recess 88-2 and the inner suction chamber communication recess 88-1, and enters the suction chamber 86. It is good also as a structure made to open. In this case, the outer suction chamber 86-2 or the inner suction chamber 86- only at the crank angle at which the suction chamber side open end 55-3b faces the outer suction chamber communication recess 88-2 or the inner suction chamber communication recess 88-1. Since oil 6 is supplied to 1, intermittent oil supply is possible.
よって、第３の経路５５−３の径や長さや、吸入室側開口端５５−３ｂの断面積や開口位置、外側吸入室連通凹部８８−２や内側吸入室連通凹部８８−１凹部の形状によって、吸入室８６へのオイル供給量を連通時間で制御できるため、吸入室８６内へのオイル６の供給量の調整範囲が広がり、吸入加熱による体積効率の悪化を抑制でき、圧縮機の効率を向上できる。 Therefore, the diameter and length of the third path 55-3, the cross-sectional area and opening position of the suction chamber side opening end 55-3b, and the shape of the outer suction chamber communication recess 88-2 and the inner suction chamber communication recess 88-1 recess. Since the amount of oil supplied to the suction chamber 86 can be controlled by the communication time, the adjustment range of the amount of oil 6 supplied to the suction chamber 86 is widened, and deterioration of volumetric efficiency due to suction heating can be suppressed. Can be improved.
なお、間欠的な給油経路は図６から図８を用いて説明した実施の形態２に示す方法で構成してもよい。 In addition, you may comprise an intermittent oil supply path | route by the method shown in Embodiment 2 demonstrated using FIGS.
（実施の形態４）
図１４と図１５は、本発明の第４の実施の形態に係るスクロール圧縮機の圧縮機構部の拡大断面図であり、図１４は内連通を示し、図１５は外連通を示す。図１４と図１５において、吸入室８６へのオイル供給について、第４の経路５５−４以外は前記実施の形態１と同様なので、図２と同じ構成要素については同じ符号を用い、第４の経路５５−４に関する説明のみを行い、他は省略する。
(Embodiment 4)
14 and 15 are enlarged cross-sectional views of the compression mechanism portion of the scroll compressor according to the fourth embodiment of the present invention. FIG. 14 shows internal communication and FIG. 15 shows external communication. 14 and 15, the oil supply to the suction chamber 86 is the same as that of the first embodiment except for the fourth path 55-4. Therefore, the same reference numerals are used for the same components as in FIG. Only the route 55-4 will be described, and the others will be omitted.
図１４に示すように、本実施の形態では、第４の経路５５−４を設けている。第４の経路５５−４の一方の端は、高圧領域側開口端５５−４ａであり、高圧領域３０に常時臨んでいる。他方の端は吸入室側開口端５５−４ｂであり、旋回スクロール１３のラップ上面に設けられており、ザグリ８７を通じて常時吸入室８６に臨んでいる。 As shown in FIG. 14, in the present embodiment, a fourth path 55-4 is provided. One end of the fourth path 55-4 is a high-pressure region side opening end 55-4 a and always faces the high-pressure region 30. The other end is the suction chamber side opening end 55-4 b, which is provided on the upper surface of the orbiting scroll 13 and faces the suction chamber 86 through the counterbore 87.
高圧領域３０に流入したオイル６は、第４の経路５５−４の高圧領域側開口端５５−４ａから第４の経路５５−４を経て、第４の経路５５−４の吸入室側開口端５５−４ｂから、ザグリ８７を経て吸入室８６に流入する。 The oil 6 that has flowed into the high pressure region 30 passes through the fourth route 55-4 from the high pressure region side open end 55-4a of the fourth route 55-4 and passes through the suction chamber side open end of the fourth route 55-4. From 55-4b, it flows into the suction chamber 86 through the counterbore 87.
図１４と図１５においても、すなわち図１１（Ａ）から（Ｄ）に示す全てのクランク角において、第４の経路５５−４の吸入室側開口端５５−４ｂは吸入室８６と常時連通状態であり、常時吸入室８６に高圧のオイル６が供給される。 14 and 15, that is, at all crank angles shown in FIGS. 11A to 11D, the suction chamber side opening end 55-4 b of the fourth path 55-4 is always in communication with the suction chamber 86. The high-pressure oil 6 is always supplied to the suction chamber 86.
よって、吸入室８６に常時高圧のオイル６が供給されることにより、差圧の大きい高負荷運転時の潤滑性能が向上し、旋回スクロール１３や固定スクロール１２のラップ上面や側面の異常磨耗が抑制でき、圧縮機の信頼性が向上できる。 Therefore, by constantly supplying the high-pressure oil 6 to the suction chamber 86, the lubrication performance at the time of high load operation with a large differential pressure is improved, and abnormal wear on the upper surface and side surfaces of the orbiting scroll 13 and the fixed scroll 12 is suppressed. And the reliability of the compressor can be improved.
高圧領域３０から吸入室８６への給油量は、第４の経路５５−４の断面積や、高圧領域側開口端５５−４ａの断面積、吸入室側開口端５５−４ｂの断面積や開口位置、ザグリ８
７の断面積や深さを変化させることで制御可能である。なお、ザグリ８７をなくしても良い。
The amount of oil supplied from the high pressure region 30 to the suction chamber 86 is the cross sectional area of the fourth path 55-4, the cross sectional area of the high pressure region side opening end 55-4a, and the cross sectional area or opening of the suction chamber side opening end 55-4b. Position, counterbore 8
It is controllable by changing the cross-sectional area and depth of 7. The counterbore 87 may be eliminated.
さらに、図１６および図１７に示すように、第４の経路の吸入室側開口端５５−４ｂを外側吸入室連通凹部８８−２と内側吸入室連通凹部８８−１を経て、吸入室８６に開口させる構成としても良い。この場合、吸入室側開口端５５−４ｂが、外側吸入室連通凹部８８−２か内側吸入室連通凹部８８−１に臨んでいるクランク角においてのみ外側吸入室８６−２もしくは内側吸入室８６−１にオイル６が給油されるので、間欠的な給油が可能となる。 Further, as shown in FIGS. 16 and 17, the suction chamber side opening end 55-4 b of the fourth path passes through the outer suction chamber communication recess 88-2 and the inner suction chamber communication recess 88-1 to the suction chamber 86. It is good also as a structure made to open. In this case, the outer suction chamber 86-2 or the inner suction chamber 86- is only at the crank angle at which the suction chamber side opening end 55-4b faces the outer suction chamber communication recess 88-2 or the inner suction chamber communication recess 88-1. Since oil 6 is supplied to 1, intermittent oil supply is possible.
よって、第４の経路５５−４の径や長さや、吸入室側開口端５５−４ｂの断面積や開口位置、外側吸入室連通凹部８８−２や内側吸入室連通凹部８８−１凹部の形状によって、吸入室８６へのオイル供給量を連通時間で制御できるため、吸入室８６内へのオイル６の供給量の調整範囲が広がり、吸入加熱による体積効率の悪化を抑制でき、圧縮機の効率を向上できる。 Therefore, the diameter and length of the fourth path 55-4, the cross-sectional area and opening position of the suction chamber side opening end 55-4b, the shape of the outer suction chamber communication recess 88-2 and the inner suction chamber communication recess 88-1 recess. Since the amount of oil supplied to the suction chamber 86 can be controlled by the communication time, the adjustment range of the amount of oil 6 supplied to the suction chamber 86 is widened, and deterioration of volumetric efficiency due to suction heating can be suppressed. Can be improved.
なお、間欠的な給油経路は図６から図８を用いて説明した実施の形態２に示す方法で構成してもよい。 In addition, you may comprise an intermittent oil supply path | route by the method shown in Embodiment 2 demonstrated using FIGS.
最後に作動流体を、高圧冷媒、例えば二酸化炭素とした場合、特に動作圧力が高いため、運転時の差圧も大きくなり、渦巻き状ラップの側面隙間から作動流体がより漏れやすくなる。すなわち本発明の効果が顕著に現れ、高効率かつ高信頼性を実現するスクロール圧縮機を提供することができる。 Finally, when the working fluid is a high-pressure refrigerant, such as carbon dioxide, the operating pressure is particularly high, so the differential pressure during operation also increases, and the working fluid is more likely to leak from the side gaps of the spiral wrap. That is, it is possible to provide a scroll compressor in which the effect of the present invention appears remarkably and achieves high efficiency and high reliability.
以上のように、本発明にかかるスクロール圧縮機は、圧縮室間の漏れ経路を考慮して、渦巻きラップ側面およびラップ先端それぞれの漏れ経路に対し、効果的かつ必要最低限のオイル供給を行うことで、シール性を確保しつつ、オイル噛み込みを抑制した高効率運転を可能とするもので、作動流体を冷媒と限ることなく、空気スクロール圧縮機、真空ポンプ、スクロール型膨張機等のスクロール流体機械の用途にも適用できる。 As described above, the scroll compressor according to the present invention effectively and minimally supplies oil to each of the spiral wrap side surface and the wrap tip leakage path in consideration of the leakage path between the compression chambers. Therefore, it is possible to achieve high-efficiency operation with oil sealing suppressed while ensuring sealing performance. Scroll fluid such as air scroll compressor, vacuum pump, scroll type expander, etc. is not limited to refrigerant. It can also be applied to machine applications.
１ 密閉容器
２ 圧縮機構
３ モータ部
４ シャフト
４ａ 偏心軸部
６ オイル
１１ 主軸受部材
１２ 固定スクロール
１３ 旋回スクロール
１３ｃ 旋回スクロールのラップ先端
１３ｄ 旋回スクロールのスラスト面
１３ｅ 旋回スクロール背面
１４ 自転拘束機構
１５ 圧縮室
１５ａ 外側圧縮室
１５ｂ 内側圧縮室
１６ 吸入パイプ
１７ 吸入口
１８ 吐出口
１９ リード弁
２０ 貯油部
２５ ポンプ
２６ オイル供給穴
２９ 背圧室
３０ 高圧領域
５５−１ 第１の経路
５５−１ａ 第１の経路の高圧領域側開口端
５５−１ｂ 第１の経路の背圧室側開口端
５５−２ 第２の経路
５５−２ａ 第２の経路の背圧室側開口端
５５−２ｂ 第２の経路の圧縮室側開口端
５５−２ｃ 内側圧縮室側開口端
５５−２ｄ 外側圧縮室側開口端
５５−３ 第３の経路
５５−３ａ 背圧室側開口端
５５−３ｂ 吸入室側開口端
５５−４ 第４の経路
５５−４ａ 高圧領域側開口端
５５−４ｂ 吸入室側開口端
６６ 軸受部
７８ シール部材
８４ 内側圧縮室連通凹部
８５ 外側圧縮室連通凹部
８６ 吸入室
８７ ザグリ
８８−１ 内側吸入室連通凹部
８８−２ 外側吸入室連通凹部
DESCRIPTION OF SYMBOLS 1 Airtight container 2 Compression mechanism 3 Motor part 4 Shaft 4a Eccentric shaft part 6 Oil 11 Main bearing member 12 Fixed scroll 13 Orbiting scroll 13c Orbiting scroll lap tip 13d Orbiting scroll thrust surface 13e Orbiting scroll back surface 14 Rotation restraint mechanism 15 Compression chamber 15a Outer compression chamber 15b Inner compression chamber 16 Suction pipe 17 Suction port 18 Discharge port 19 Reed valve 20 Oil reservoir 25 Pump 26 Oil supply hole 29 Back pressure chamber 30 High pressure region 55-1 First path 55-1a First path High pressure region side open end 55-1b Back pressure chamber side open end of first path 55-2 Second path 55-2a Back pressure chamber side open end of second path 55-2b Compression of second path Chamber side opening end 55-2c Inner compression chamber side opening end 55-2d Outer compression chamber side opening end 55-3 Third path 55 3a Back pressure chamber side opening end 55-3b Suction chamber side opening end 55-4 Fourth path 55-4a High pressure region side opening end 55-4b Suction chamber side opening end 66 Bearing portion 78 Seal member 84 Inner compression chamber communication recess 85 Outer compression chamber communication recess 86 Suction chamber 87 Counterbore 88-1 Inner suction chamber communication recess 88-2 Outer suction chamber communication recess
Claims (10)
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009022135A JP5304285B2 (en) | 2009-02-03 | 2009-02-03 | Scroll compressor |
| CN200980114359.9A CN102016319B (en) | 2008-04-22 | 2009-04-20 | Scroll compressor |
| AU2009239310A AU2009239310A1 (en) | 2008-04-22 | 2009-04-20 | Scroll compressor |
| PCT/JP2009/001799 WO2009130878A1 (en) | 2008-04-22 | 2009-04-20 | Scroll compressor |
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| JP2009022135A JP5304285B2 (en) | 2009-02-03 | 2009-02-03 | Scroll compressor |
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|---|---|
| JP2010180703A true JP2010180703A (en) | 2010-08-19 |
| JP5304285B2 JP5304285B2 (en) | 2013-10-02 |
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| Application Number | Title | Priority Date | Filing Date |
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| JP2009022135A Active JP5304285B2 (en) | 2008-04-22 | 2009-02-03 | Scroll compressor |
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| JP (1) | JP5304285B2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012042825A1 (en) * | 2010-09-27 | 2012-04-05 | パナソニック株式会社 | Rotary compressor |
| JP2012092773A (en) * | 2010-10-28 | 2012-05-17 | Hitachi Appliances Inc | Scroll compressor |
| CN103089620A (en) * | 2012-11-14 | 2013-05-08 | 柳州易舟汽车空调有限公司 | Scroll compressor |
| JP2013167168A (en) * | 2012-02-14 | 2013-08-29 | Hitachi Appliances Inc | Scroll compressor |
| WO2021228459A1 (en) * | 2020-05-14 | 2021-11-18 | Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg | Scroll compressor of an electrical refrigerant drive |
| JP7373939B2 (en) | 2019-08-08 | 2023-11-06 | 日立ジョンソンコントロールズ空調株式会社 | scroll compressor |
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| JPH08303369A (en) * | 1996-06-14 | 1996-11-19 | Matsushita Electric Ind Co Ltd | Scroll gas compressor |
| JP2003172276A (en) * | 2001-12-03 | 2003-06-20 | Hitachi Ltd | Scroll fluid machine |
| JP2005147101A (en) * | 2003-11-20 | 2005-06-09 | Mitsubishi Electric Corp | Scroll compressor and refrigerating air conditioner |
| JP2007270697A (en) * | 2006-03-31 | 2007-10-18 | Hitachi Ltd | Scroll fluid machine |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08303369A (en) * | 1996-06-14 | 1996-11-19 | Matsushita Electric Ind Co Ltd | Scroll gas compressor |
| JP2003172276A (en) * | 2001-12-03 | 2003-06-20 | Hitachi Ltd | Scroll fluid machine |
| JP2005147101A (en) * | 2003-11-20 | 2005-06-09 | Mitsubishi Electric Corp | Scroll compressor and refrigerating air conditioner |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012042825A1 (en) * | 2010-09-27 | 2012-04-05 | パナソニック株式会社 | Rotary compressor |
| JPWO2012042825A1 (en) * | 2010-09-27 | 2014-02-03 | パナソニック株式会社 | Rotary compressor |
| JP2012092773A (en) * | 2010-10-28 | 2012-05-17 | Hitachi Appliances Inc | Scroll compressor |
| JP2013167168A (en) * | 2012-02-14 | 2013-08-29 | Hitachi Appliances Inc | Scroll compressor |
| CN103089620A (en) * | 2012-11-14 | 2013-05-08 | 柳州易舟汽车空调有限公司 | Scroll compressor |
| JP7373939B2 (en) | 2019-08-08 | 2023-11-06 | 日立ジョンソンコントロールズ空調株式会社 | scroll compressor |
| WO2021228459A1 (en) * | 2020-05-14 | 2021-11-18 | Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg | Scroll compressor of an electrical refrigerant drive |
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|---|---|
| JP5304285B2 (en) | 2013-10-02 |
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