JP4519489B2 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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JP4519489B2
JP4519489B2 JP2004073092A JP2004073092A JP4519489B2 JP 4519489 B2 JP4519489 B2 JP 4519489B2 JP 2004073092 A JP2004073092 A JP 2004073092A JP 2004073092 A JP2004073092 A JP 2004073092A JP 4519489 B2 JP4519489 B2 JP 4519489B2
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back pressure
pressure
chamber
scroll
compression
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JP2005256809A (en
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雅嗣 近野
健一 大島
康弘 岸
昌浩 島田
英治 佐藤
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Hitachi Appliances Inc
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Hitachi Appliances Inc
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Priority to JP2004073092A priority Critical patent/JP4519489B2/en
Priority to CNB2005100550229A priority patent/CN100362238C/en
Priority to KR1020050020834A priority patent/KR100604282B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Description

本発明は、スクロール圧縮機に関する。   The present invention relates to a scroll compressor.

スクロール圧縮機は、鏡板に渦巻状のラップをそれぞれ立設してなる固定スクロールと旋回スクロールとを、ラップを噛み合わせて対向させて配置し、旋回スクロールを旋回させて互いのラップ間に形成される複数の圧縮室の容積を順次縮小させることにより流体を圧縮するようにしている。この圧縮作用により、固定スクロールと旋回スクロールを互いに引き離そうとする軸方向の力（以下、引離し力という。）が発生する。両スクロールが引き離されてしまうと、ラップの歯先と鏡板との間にギャップが生じて圧縮室の密閉性が悪化して、圧縮機の効率が低下する。そこで、旋回スクロールの鏡板の背面に背圧室を形成し、その背圧室に圧縮機の吐出圧と吸込圧の中間圧力を背圧として導入し、背圧により旋回スクロールを固定スクロール側に押圧して、引離し力を打ち消すとともに、固定スクロールと旋回スクロール間に引付力を発生させている。   A scroll compressor is formed between a wrap and a fixed scroll, which is formed by standing a spiral wrap on the end plate, and a orbiting scroll, with the wrap meshing and facing each other. The fluid is compressed by sequentially reducing the volumes of the plurality of compression chambers. Due to this compression action, an axial force (hereinafter referred to as a pulling force) for generating the fixed scroll and the orbiting scroll apart from each other is generated. If both scrolls are pulled apart, a gap is generated between the tooth tip of the wrap and the end plate, the sealing performance of the compression chamber is deteriorated, and the efficiency of the compressor is lowered. Therefore, a back pressure chamber is formed on the back of the end plate of the orbiting scroll, an intermediate pressure between the discharge pressure and suction pressure of the compressor is introduced as a back pressure into the back pressure chamber, and the orbiting scroll is pressed to the fixed scroll side by the back pressure. Thus, the pulling force is canceled and an attractive force is generated between the fixed scroll and the orbiting scroll.

しかし、引付力が大きすぎると旋回スクロールと固定スクロールとの間のスラスト力が大きくなり、各ラップの歯先と歯底の摺動摩擦が増大し、圧縮機の効率が低下する。そこで、引付力を適当な大きさに調整する必要があることから、特許文献１に記載のスクロール圧縮機では、背圧室と吸込室とを背圧調整弁を介して連通し、背圧室と吸込室との圧力差に応じて背圧室の流体を吸込室に逃がして背圧の大きさを調整している。   However, if the attraction force is too large, the thrust force between the orbiting scroll and the fixed scroll increases, the sliding friction between the tooth tip and the tooth bottom of each lap increases, and the efficiency of the compressor decreases. Therefore, since it is necessary to adjust the attractive force to an appropriate magnitude, in the scroll compressor described in Patent Document 1, the back pressure chamber and the suction chamber are communicated with each other via a back pressure adjustment valve. The magnitude of the back pressure is adjusted by allowing the fluid in the back pressure chamber to escape into the suction chamber in accordance with the pressure difference between the chamber and the suction chamber.

特開平１０−１１０６８８号公報JP-A-10-110688

しかし、特許文献１に記載の背圧調整法によれば、一度圧縮して得られる中間圧力の流体を膨張させて吸込室に戻すことになるから、スクロール圧縮機の全体からみて圧縮損失が発生することになり、圧縮機の効率が低下するという問題がある。   However, according to the back pressure adjustment method described in Patent Document 1, the intermediate pressure fluid obtained by compressing once is expanded and returned to the suction chamber, so that a compression loss occurs from the whole scroll compressor. Therefore, there is a problem that the efficiency of the compressor is lowered.

また、特許文献１に記載の背圧調整法によれば、背圧＝吸込圧＋α（一定値）に自動調整されるが、圧縮機の運転条件によっては、最適な背圧値が吸込圧＋αから大きくずれる場合がある。その結果、背圧が過大のときは摺動損失が増大し、過小のときは漏れ損失が増大するため、いずれにしても圧縮機の効率が低下するという問題がある。   Further, according to the back pressure adjustment method described in Patent Document 1, the back pressure is automatically adjusted to the suction pressure + α (a constant value). However, depending on the operating conditions of the compressor, the optimum back pressure value may be the suction pressure + α. May deviate greatly. As a result, the sliding loss increases when the back pressure is excessive, and the leakage loss increases when the back pressure is excessive. Therefore, there is a problem that the efficiency of the compressor is reduced in any case.

本発明は、固定スクロールと旋回スクロールの引付力を調整する背圧調整に伴う損失を低減することを課題とする。   This invention makes it a subject to reduce the loss accompanying back pressure adjustment which adjusts the attractive force of a fixed scroll and a turning scroll.

本発明は、上記課題を解決するため、鏡板に渦巻状のラップが立設された固定スクロールと、該固定スクロールに対向して旋回可能に設けられ、前記固定スクロールのラップとの間に複数の圧縮室を形成する渦巻状のラップが立設された旋回スクロールと、前記旋回スクロールの背面に設けられ吐出圧と吸込圧の中間圧力が導入される背圧室と、前記固定スクロールの最外周ラップの歯先に形成された連通路を介して導入される吸込圧力または圧縮初期圧力と前記背圧室の圧力との差に応じて、前記背圧室の流体を前記連通路を介して前記吸込室または圧縮初期の圧縮室に逃す背圧調整弁と、前記固定スクロールと前記旋回スクロールを収納する密閉容器に貯留される潤滑油を前記背圧室に流入させる潤滑油供給手段とを備え、前記連通路に連通していない圧縮室と前記背圧室とを連通する貫通孔を前記旋回スクロールに設けてなり、前記貫通孔は、前記背圧室に面する前記旋回スクロールの鏡板から前記ラップの歯先まで貫通して形成されてなることを特徴とする。 In order to solve the above-mentioned problems, the present invention provides a fixed scroll in which a spiral wrap is erected on an end plate, and is provided so as to be able to turn opposite to the fixed scroll, and a plurality of spaces are provided between the fixed scroll wrap. An orbiting scroll provided with a spiral wrap that forms a compression chamber, a back pressure chamber that is provided on the back surface of the orbiting scroll and into which an intermediate pressure between discharge pressure and suction pressure is introduced, and an outermost peripheral wrap of the fixed scroll In response to the difference between the suction pressure or the compression initial pressure introduced through the communication passage formed in the tooth tip of the tooth and the pressure in the back pressure chamber, the fluid in the back pressure chamber is sucked through the communication passage. A back pressure regulating valve that escapes to the compression chamber in the chamber or the initial stage of compression, and a lubricating oil supply means that causes the lubricating oil stored in a sealed container that houses the fixed scroll and the orbiting scroll to flow into the back pressure chamber, In the passage Through though not the compression chamber through hole communicating with the back pressure chamber becomes disposed in said orbiting scroll, said through-hole, through the end plate of said orbiting scroll facing said back pressure chamber to the tooth tip of the lap It is characterized by being formed .

このように、旋回スクロールに背圧室と圧縮室とを連通する貫通孔を設けたことから、背圧室の圧力が過大になった場合、背圧室内の流体は、背圧調整弁と連通路を介して吸込室または圧縮初期の圧縮室に流出すると同時に、一部は貫通孔を通って吸込室または圧縮初期の圧縮室の圧力よりも高い圧縮室に流出する。その結果、背圧調整のために、一度圧縮して得られる背圧室の流体を吸込室または圧縮初期の圧縮室に全量逃す場合の膨張損失に比べて、一部を吸込室の圧力よりも高い圧縮室に逃すことになるから、スクロール圧縮機の全体からみた損失を低減することができる。   As described above, since the orbiting scroll is provided with a through-hole that communicates the back pressure chamber and the compression chamber, when the pressure in the back pressure chamber becomes excessive, the fluid in the back pressure chamber communicates with the back pressure adjustment valve. At the same time as flowing out to the suction chamber or the compression chamber in the initial stage of compression through the passage, a part flows out to the compression chamber having a pressure higher than the pressure of the suction chamber or the compression chamber in the initial stage of compression through the through hole. As a result, in order to adjust the back pressure, compared with the expansion loss when all the fluid in the back pressure chamber obtained by compression once is released to the suction chamber or the compression chamber at the initial stage of compression, a part of the fluid is more than the pressure in the suction chamber. Since the high compression chamber is missed, the loss seen from the whole scroll compressor can be reduced.

この場合において、貫通孔は、背圧室に面する旋回スクロールの鏡板からラップの歯先まで貫通して形成することが好ましい。また、背圧室に面する旋回スクロールの鏡板に形成することができる。いずれの場合においても、圧縮室に通じる側の貫通孔の孔径が、背圧室に通じる側の孔径より小さいことが好ましい。   In this case, the through hole is preferably formed to penetrate from the end plate of the orbiting scroll facing the back pressure chamber to the tooth tip of the wrap. Moreover, it can form in the end plate of the turning scroll which faces a back pressure chamber. In any case, it is preferable that the hole diameter of the through hole on the side leading to the compression chamber is smaller than the hole diameter on the side leading to the back pressure chamber.

特に、貫通孔を旋回スクロールの鏡板からラップの歯先まで貫通して設けた場合、背圧室内の流体が貫通孔を通って圧縮室に入るときに、ラップの歯先が摺動する固定スクロールの鏡板（歯底部）との微小な隙間を通ることになる。この隙間が流路抵抗となるため、背圧室と圧縮室を直接連通する場合に比べて、流体の自由な流出入を抑制できるから、背圧室内の圧力変動を小さく抑えることができる。また、旋回スクロールが１回転する間に、背圧室から圧縮室へ、圧縮室から背圧室へと流れの向きが毎回変わることになるが、これによる圧縮損失（いわゆる呼吸損失）を小さく抑えることができる。   In particular, when a through hole is provided to penetrate from the end plate of the orbiting scroll to the tip of the wrap, the fixed scroll in which the tip of the wrap slides when the fluid in the back pressure chamber enters the compression chamber through the through hole. It passes through a minute gap with the end plate (tooth bottom). Since this gap serves as a flow path resistance, the fluid can be prevented from freely flowing in and out as compared with the case where the back pressure chamber and the compression chamber are directly communicated with each other, so that the pressure fluctuation in the back pressure chamber can be suppressed. In addition, the flow direction changes from the back pressure chamber to the compression chamber, and from the compression chamber to the back pressure chamber each time during one revolution of the orbiting scroll, but the compression loss (so-called breathing loss) due to this is kept small. be able to.

本発明によれば、固定スクロールと旋回スクロールの引付力を調整する背圧調整に伴う損失を低減することができる。   ADVANTAGE OF THE INVENTION According to this invention, the loss accompanying the back pressure adjustment which adjusts the attractive force of a fixed scroll and a turning scroll can be reduced.

以下、本発明の一実施の形態を、図面を参照して説明する。図１は本実施の形態のスクロール圧縮機の全体を示す断面図である。図２（Ａ）は本実施の形態の特徴部に係る旋回スクロールのラップ側から見た平面図であり、同図（Ｂ）は図１（Ａ）の線Ｂ−Ｂにおける断面図である。   Hereinafter, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a cross-sectional view showing the entire scroll compressor according to the present embodiment. 2A is a plan view seen from the wrap side of the orbiting scroll according to the characterizing portion of the present embodiment, and FIG. 2B is a cross-sectional view taken along line BB in FIG.

図１に示すように、固定スクロール７は円板状に形成された鏡板７ａと、この鏡板７ａの上に渦巻状に立設されたラップ７ｂと、鏡板７ａの外周側に位置し、ラップ７ｂを囲むように筒状に形成された支持部７ｄとから構成されている。ラップ７ｂが立設された鏡板７ａの表面は、歯底７ｃとなっている。また、固定スクロール７は、支持部７ｄでボルト等によりフレーム１７に固定されており、固定スクロール７と一体となったフレーム１７は、溶接等の固定手段によりケーシング９に固定されている。   As shown in FIG. 1, the fixed scroll 7 is located on the outer peripheral side of the end plate 7a, the end plate 7a formed in a disc shape, the wrap 7b erected on the end plate 7a in a spiral shape, and the wrap 7b. It is comprised from the support part 7d formed in the cylinder shape so that may be enclosed. The surface of the end plate 7a on which the wrap 7b is erected is a tooth bottom 7c. The fixed scroll 7 is fixed to the frame 17 by bolts or the like at the support portion 7d, and the frame 17 integrated with the fixed scroll 7 is fixed to the casing 9 by fixing means such as welding.

一方、旋回スクロール８は、固定スクロール７に対向して配置され、フレーム１７内に旋回可能に設けられている。旋回スクロール８は、円板状の鏡板８ａと、固定スクロール７のラップ７ｂと同様に、鏡板８ａの表面である歯底８ｃから立設された渦巻状のラップ８ｂと、鏡板８ａの背面中央に設けられたボス部８ｄとを有して構成されている。   On the other hand, the orbiting scroll 8 is disposed to face the fixed scroll 7 and is provided in the frame 17 so as to be orbitable. Similar to the disc-shaped end plate 8a and the wrap 7b of the fixed scroll 7, the orbiting scroll 8 has a spiral wrap 8b erected from the tooth bottom 8c, which is the surface of the end plate 8a, and the back center of the end plate 8a. And a boss portion 8d provided.

ケーシング９は、固定スクロール７と旋回スクロール８からなるスクロール部、モータ１６、および潤滑油を内部に収納して、密閉構造に形成されている。モータ１６の回転子１６ａを備えたシャフト１０は、フレーム１７に回転自在に設けられ、固定スクロール７の軸線と同軸となっている。シャフト１０の先端にはクランク１０ａが設けられており、クランク１０ａに旋回軸受１１を介して旋回スクロール８のボス部８ｄが回転可能に取り付けられている。旋回スクロール８は、軸線が固定スクロール７の軸線に対して所定距離δだけ偏心した状態に取り付けられている。また、旋回スクロール８のラップ８ｂは、固定スクロール７のラップ７ｂに周方向に所定角度だけずらして重ね合わせられている。そして、旋回スクロール８を固定スクロール７に対して自転しないように拘束しながら相対的に旋回運動させるための機構として、オルダムリング１２が取り付けられている。この状態で旋回スクロール８を旋回運動させたとき、ラップ７ｂ、８ｂ間に、中央部に移動するに従い連続的に容積が縮小される三日月状の複数の圧縮室１３が形成される。例えば、非対称ラップの場合、図３に示すように、旋回スクロール８の内線側及び外線側に、それぞれ旋回内線側圧縮室１３ａ及び旋回外線側圧縮室１３ｂが形成される。   The casing 9 is formed in a hermetically sealed structure that houses a scroll portion including the fixed scroll 7 and the orbiting scroll 8, a motor 16, and lubricating oil. The shaft 10 including the rotor 16 a of the motor 16 is rotatably provided on the frame 17 and is coaxial with the axis of the fixed scroll 7. A crank 10 a is provided at the tip of the shaft 10, and a boss portion 8 d of the orbiting scroll 8 is rotatably attached to the crank 10 a via an orbiting bearing 11. The orbiting scroll 8 is attached so that its axis is eccentric by a predetermined distance δ with respect to the axis of the fixed scroll 7. The wrap 8b of the orbiting scroll 8 is overlapped with the wrap 7b of the fixed scroll 7 while being shifted by a predetermined angle in the circumferential direction. An Oldham ring 12 is attached as a mechanism for causing the orbiting scroll 8 to orbit relative to the fixed scroll 7 while restraining it from rotating. When the orbiting scroll 8 is orbited in this state, a plurality of crescent-shaped compression chambers 13 are formed between the wraps 7b and 8b whose volume is continuously reduced as they move to the center. For example, in the case of an asymmetric wrap, as shown in FIG. 3, a turning extension side compression chamber 13a and a turning outer line side compression chamber 13b are formed on the inner line side and the outer line side of the orbiting scroll 8, respectively.

吸入ポート１４は、固定スクロール７に形成されており、この吸入ポート１４は最外周側の圧縮室１３と連通するように鏡板７ａの外周側に穿設され、吸込室が形成されている。また、吐出ポート１５は、最内周側の圧縮室１３と連通するように固定スクロール７の鏡板７ａの中心部に穿設され、吐出室が形成されている。   The suction port 14 is formed in the fixed scroll 7. The suction port 14 is formed on the outer peripheral side of the end plate 7a so as to communicate with the outermost peripheral compression chamber 13, thereby forming a suction chamber. Further, the discharge port 15 is formed in the center portion of the end plate 7a of the fixed scroll 7 so as to communicate with the innermost peripheral compression chamber 13 to form a discharge chamber.

ここで、本実施の形態の特徴構成について説明する。図２（Ａ）、（Ｂ）および図１に示すように、旋回スクロール８のラップ８ｂに、背圧室１８と圧縮室１３を連通するように貫通孔１が設けられている。すなわち、貫通孔１は、図２（Ｂ）に示すように、背圧室１８に面する旋回スクロールの鏡板８ａからラップ８ｂの歯先まで貫通して形成されている。貫通孔１のラップ８ｂ上の位置は、貫通孔１の圧縮室１３側の圧力が適当な背圧値に近い値になる位置としている。例えば、図３に示すように、貫通孔１の圧縮室１３側の圧力は、旋回内線側圧縮室１３ａと旋回外線側圧縮室１３ｂの圧力の中間の値となる。なお、旋回内線側圧縮室１３ａおよび旋回外線側圧縮室１３ｂ内の圧力は、旋回スクロール８が１旋回する間に変動するから、１旋回中のそれぞれの平均圧力の中間の値が貫通孔１の圧縮室１３側の圧力となる。   Here, the characteristic configuration of the present embodiment will be described. As shown in FIGS. 2A, 2 </ b> B, and 1, the through hole 1 is provided in the wrap 8 b of the orbiting scroll 8 so as to communicate the back pressure chamber 18 and the compression chamber 13. That is, as shown in FIG. 2B, the through hole 1 is formed to penetrate from the end plate 8a of the orbiting scroll facing the back pressure chamber 18 to the tooth tip of the wrap 8b. The position of the through hole 1 on the wrap 8b is a position at which the pressure on the compression chamber 13 side of the through hole 1 becomes a value close to an appropriate back pressure value. For example, as shown in FIG. 3, the pressure on the compression chamber 13 side of the through-hole 1 is an intermediate value between the pressures in the turning inner line side compression chamber 13 a and the turning outer line side compression chamber 13 b. Note that the pressures in the orbiting inner compression chamber 13a and the orbiting outer compression chamber 13b fluctuate while the orbiting scroll 8 makes one revolution, so that the mean value of each average pressure during one revolution is the value of the through hole 1. The pressure is on the compression chamber 13 side.

また、貫通孔１は、図２（Ｂ）に示すように、圧縮室１３に通じる側の孔径ｄ１が背圧室１８に通じる側の孔径ｄ２より小さく形成されている。つまり、固定スクロール７の歯底と摺動するラップ８ｂの歯幅が、貫通孔１によって減少するのをできるだけ抑えるようにしている。   Further, as shown in FIG. 2B, the through hole 1 is formed such that the hole diameter d 1 on the side communicating with the compression chamber 13 is smaller than the hole diameter d 2 on the side communicating with the back pressure chamber 18. In other words, the tooth width of the wrap 8 b that slides with the tooth bottom of the fixed scroll 7 is suppressed as much as possible from being reduced by the through hole 1.

このように構成される本実施の形態のスクロール圧縮機の作動について説明する。まず、モータ１６によってシャフト１０を回転駆動すると、この回転はシャフト１０のクランク１０ａから旋回軸受１１を介して旋回スクロール８に伝えられる。これにより、旋回スクロール８は固定スクロール７の軸線を中心に、所定距離δの旋回半径をもって旋回運動する。この旋回運動時に旋回スクロール８が自転しないように、オルダムリング１２によって拘束される。そして、旋回スクロール８の旋回運動によって、各ラップ７ｂ、８ｂの間にできる圧縮室１３は中央に連続的に移動し、その移動に従って圧縮室１３の容積が連続的に縮小する。これによって、吸入ポート１４から吸込まれた流体を各圧縮室１３内で順次圧縮し、圧縮された流体は吐出ポート１５から吐出される。吐出された流体は、ケーシング９内を通って吐出パイプ６から、例えば冷凍サイクルに供給される。 The operation of the scroll compressor of the present embodiment configured as described above will be described. First, when the shaft 10 is rotationally driven by the motor 16, this rotation is transmitted from the crank 10 a of the shaft 10 to the orbiting scroll 8 via the orbiting bearing 11. As a result, the orbiting scroll 8 orbits around the axis of the fixed scroll 7 with an orbiting radius of a predetermined distance δ. It is restrained by the Oldham ring 12 so that the turning scroll 8 does not rotate during this turning motion. Then, due to the orbiting motion of the orbiting scroll 8, the compression chamber 13 formed between the wraps 7b and 8b continuously moves to the center, and the volume of the compression chamber 13 is continuously reduced according to the movement. Thus, the fluid sucked from the suction port 14 is sequentially compressed in each compression chamber 13, and the compressed fluid is discharged from the discharge port 15. The discharged fluid passes through the casing 9 and is supplied from the discharge pipe 6 to, for example, a refrigeration cycle.

一方、潤滑油はケーシング９の底に貯留され、周囲の圧力は吐出圧になっている。背圧室１８内の圧力は吐出圧より低いため、ケーシング９の底に貯留している潤滑油はシャフト１０に設けた貫通孔３を通って背圧室１８に流入する。具体的には、潤滑油の一部はシャフト１０に設けた横穴４を通って主軸受５を潤滑しながら背圧室１８に達する。また、他の潤滑油は、貫通孔３を通ってシャフト１０のクランク１０ａ上部に達し、旋回軸受１１を潤滑して背圧室１８に入る。ここで、潤滑油は、主軸受５および旋回軸受１１を通過する際、軸受隙間が小さいため絞られて吐出圧より低い圧力で背圧室１８に入ることになる。背圧室１８に入った潤滑油は、背圧が高くなると、吸込室への連通路に設けられた背圧調整弁２を開いて吸込室へ入る。そして、圧縮室１３を通って吐出ポート１５から吐出され、一部は吐出パイプ６から冷凍サイクルへ吐出され、残りはケーシング９内で冷媒と分離されて底に貯留する。 On the other hand, the lubricating oil is stored at the bottom of the casing 9, and the surrounding pressure is the discharge pressure. Since the pressure in the back pressure chamber 18 is lower than the discharge pressure, the lubricating oil stored at the bottom of the casing 9 flows into the back pressure chamber 18 through the through hole 3 provided in the shaft 10. Specifically, part of the lubricating oil reaches the back pressure chamber 18 while lubricating the main bearing 5 through the lateral hole 4 provided in the shaft 10. Other lubricating oil passes through the through hole 3 and reaches the upper part of the crank 10 a of the shaft 10, lubricates the swivel bearing 11 and enters the back pressure chamber 18. Here, when the lubricating oil passes through the main bearing 5 and the slewing bearing 11, the bearing clearance is small, so that the lubricating oil enters the back pressure chamber 18 at a pressure lower than the discharge pressure. When the back pressure increases, the lubricating oil that has entered the back pressure chamber 18 opens the back pressure adjustment valve 2 provided in the communication path to the suction chamber and enters the suction chamber. And it discharges from the discharge port 15 through the compression chamber 13, and a part is discharged from the discharge pipe 6 to a refrigerating cycle, and the remainder is isolate | separated from a refrigerant | coolant within the casing 9, and is stored in the bottom.

ここで、図４、図５により背圧調整弁２の構成および作動について説明する。背圧調整弁２は、背圧室１８と通じている空間２ｄと、固定スクロール７の最外周のラップ７ｅの歯先に設けられた連通路２ｆにより吸込室（または、圧縮初期の圧縮室１３）に通じている空間２ｅを仕切るように弁体２ａが配置されている。弁体２ａはバネ２ｂにより空間２ｄに連通する開口部に押し付けられている。弁体２ａは、空間２ｄ内の圧力が、連通路２ｆを介して導入される空間２ｅ内の吸込室または圧縮初期の圧縮室の圧力と、バネ２ｂの押付け力に対応する圧力の合計より高くなった場合に、上方へ移動して空間２ｄと空間２ｅを連通させる。これによって、背圧室の圧力（背圧）Ｐｂは、吸込室の圧力（吸込圧）または圧縮初期の圧縮室の圧力をＰｓとし、バネ２ｂの押付け力に対応する圧力をα（一定値）とすると、次式１のように制御される。   Here, the configuration and operation of the back pressure adjusting valve 2 will be described with reference to FIGS. The back pressure regulating valve 2 has a suction chamber (or a compression chamber 13 at the initial compression stage) by a space 2d communicating with the back pressure chamber 18 and a communication passage 2f provided at the tooth tip of the outermost lap 7e of the fixed scroll 7. The valve body 2a is arranged so as to partition the space 2e that communicates with. The valve body 2a is pressed against the opening communicating with the space 2d by a spring 2b. In the valve body 2a, the pressure in the space 2d is higher than the sum of the pressure corresponding to the pressing force of the spring 2b and the pressure in the suction chamber or the compression chamber in the initial stage of compression in the space 2e introduced through the communication passage 2f. When it becomes, it moves upward and makes the space 2d and the space 2e communicate. As a result, the pressure (back pressure) Pb in the back pressure chamber is set to Ps as the pressure in the suction chamber (suction pressure) or the pressure in the compression chamber at the initial stage of compression, and the pressure corresponding to the pressing force of the spring 2b is α (constant value). Then, control is performed as in the following equation 1.

（数１）
Ｐｂ＝Ｐｓ＋α
次に、本実施の形態の特徴構成の作用について説明する。まず、背圧室１８に常に流れ込んでくる潤滑油およびそれに溶け込んだ冷媒により背圧が高くなった場合、背圧室１８内の流体の一部は貫通孔１を通って圧縮室１３内に流入する。これとともに、背圧室１８内の流体は背圧調整弁２を通って吸込室または吸込圧よりわずかに圧力が高くなった初期圧縮状態の圧縮室１３内に流入する。ここで、背圧が上昇して背圧調整弁２が開くということは、一度圧縮した流体が吸込圧またはそれに近い圧縮室内圧力まで再膨張するということであるから、圧縮損失が生じることになる。この点、本実施の形態では、背圧室１８内の流体が全て背圧調整弁２を通って吸込圧またはそれに近い圧縮室内圧力まで再膨張するわけではなく、その一部は貫通孔１を通って背圧に近い圧力まで上昇した圧縮室１３へ入るので、再膨張損失を低減でき圧縮効率の高いスクロール圧縮機を実現できる。また、旋回スクロール８に貫通孔１を設けるだけであるので、大幅なコストの上昇は生じない。 (Equation 1)
Pb = Ps + α
Next, the operation of the characteristic configuration of the present embodiment will be described. First, when the back pressure is increased by the lubricating oil constantly flowing into the back pressure chamber 18 and the refrigerant dissolved therein, a part of the fluid in the back pressure chamber 18 flows into the compression chamber 13 through the through hole 1. To do. At the same time, the fluid in the back pressure chamber 18 flows through the back pressure regulating valve 2 into the suction chamber or the compression chamber 13 in the initial compression state in which the pressure is slightly higher than the suction pressure. Here, when the back pressure rises and the back pressure adjustment valve 2 opens, it means that the fluid once compressed is re-expanded to the suction pressure or the pressure in the compression chamber close thereto, so that a compression loss occurs. . In this respect, in the present embodiment, not all the fluid in the back pressure chamber 18 re-expands to the suction pressure or the compression chamber pressure close to the suction pressure adjusting valve 2, and a part of the fluid passes through the through hole 1. Since it enters the compression chamber 13 that has passed through and increased to a pressure close to the back pressure, a re-expansion loss can be reduced, and a scroll compressor with high compression efficiency can be realized. Further, since only the through hole 1 is provided in the orbiting scroll 8, there is no significant cost increase.

また、本実施の形態では、旋回スクロール８のラップ８ｂに貫通孔１を設けているため、背圧室１８内の流体が貫通孔１を通って圧縮室１３に入るときに、旋回スクロール８のラップ８ｂの歯先と、固定スクロール７の歯底７ｃとの微小な隙間を通ることになる。この隙間が流路抵抗となり、背圧室１８と圧縮室１３を直接連通する場合に比べて、流体の自由な流出入を抑制できるから、背圧室１８内の圧力変動を小さく抑えることができる。また、旋回スクロール８が１旋回する間に、背圧室１８から圧縮室１３へ、圧縮室１３から背圧室１８へと流れの向きが毎回変わることになるが、これによる圧縮損失（いわゆる呼吸損失）を小さく抑えることができる。   In the present embodiment, since the through hole 1 is provided in the wrap 8 b of the orbiting scroll 8, when the fluid in the back pressure chamber 18 enters the compression chamber 13 through the through hole 1, It passes through a minute gap between the tooth tip of the wrap 8b and the tooth bottom 7c of the fixed scroll 7. This gap serves as a flow path resistance, and the free flow of fluid can be suppressed compared to the case where the back pressure chamber 18 and the compression chamber 13 are directly communicated with each other. . Further, while the orbiting scroll 8 makes one revolution, the flow direction changes from the back pressure chamber 18 to the compression chamber 13 and from the compression chamber 13 to the back pressure chamber 18 every time. Loss) can be kept small.

さらに、図６を参照して、本発明の背圧調整の動作について説明する。図６は、背圧Ｐｂと吸込圧Ｐｓの関係を模式的に表したグラフであり、横軸は吸込圧Ｐｓ、縦軸は背圧Ｐｂを示している。圧縮機のある運転条件において、背圧Ｐｂが過大のとき摺動損失が増大し、過小のとき漏れ損失が増大するため、最適な背圧値が存在する。その最適な背圧値は、圧縮機の様々な運転条件により異なった値をとる。圧縮機の代表的な運転条件に対する最適な背圧値を、模式的にプロットしたのが図中の点１９ａ〜１９ｄである。   Furthermore, with reference to FIG. 6, the operation | movement of the back pressure adjustment of this invention is demonstrated. FIG. 6 is a graph schematically showing the relationship between the back pressure Pb and the suction pressure Ps. The horizontal axis represents the suction pressure Ps, and the vertical axis represents the back pressure Pb. Under certain operating conditions of the compressor, the sliding loss increases when the back pressure Pb is excessive, and the leakage loss increases when the back pressure Pb is excessive. The optimum back pressure value varies depending on various operating conditions of the compressor. Points 19a to 19d in the figure are schematically plotted the optimum back pressure values for typical operating conditions of the compressor.

いま、背圧室と吸込室を連通させる背圧調整弁２を用いて背圧を調整する場合、前記式１のとおり、Ｐｂ＝Ｐｓ＋αとなり、図中の線Ｃ−Ｅ−Ｄで表せる。なお、背圧調整弁２を、吸込圧よりわずかに圧力が高くなった初期圧縮状態の圧縮室に連通する場合は、Ｐｂ＝ｋ・Ｐｓ＋αとなり、図示していないが、線Ｃ−Ｅ−Ｄよりも上方に移動した直線で表される。ここで、ｋは、初期圧縮状態の圧縮係数である。   Now, when the back pressure is adjusted using the back pressure regulating valve 2 that allows the back pressure chamber and the suction chamber to communicate with each other, Pb = Ps + α as shown in the above equation 1, which can be represented by the line CED in the figure. When the back pressure adjusting valve 2 communicates with the compression chamber in the initial compression state in which the pressure is slightly higher than the suction pressure, Pb = k · Ps + α, which is not shown, but is not shown. It is represented by a straight line moved upward. Here, k is a compression coefficient in the initial compression state.

ここで、背圧室と吸込室を連通させる背圧調整弁２により背圧を調整する場合についてみると、点１９ａ、点１９ｂでは最適な背圧値とほぼ一致しているが、点１９ｃ、点１９ｄにおいて背圧Ｐｂは最適値よりも過大となっている。一方、旋回スクロール８に設けた貫通孔１により背圧を調整する場合、背圧Ｐｂは貫通孔１と通じる圧縮室１３の平均圧力となるから、吸込圧Ｐｓに、圧縮室１３の平均圧力に相当する一定の圧縮係数βを乗じて、次式２で表すことができる。   Here, in the case where the back pressure is adjusted by the back pressure regulating valve 2 that allows the back pressure chamber and the suction chamber to communicate with each other, the points 19a and 19b substantially coincide with the optimum back pressure values. At the point 19d, the back pressure Pb is larger than the optimum value. On the other hand, when the back pressure is adjusted by the through hole 1 provided in the orbiting scroll 8, the back pressure Pb becomes the average pressure of the compression chamber 13 communicating with the through hole 1, so that the suction pressure Ps becomes the average pressure of the compression chamber 13. Multiplication by a corresponding constant compression coefficient β can be expressed by the following equation 2.

（数２）
Ｐｂ＝Ｐｓ×β
このときの背圧Ｐｂは、図中の線Ａ−Ｅ−Ｂの直線で表せる。この線Ａ−Ｅ−Ｂは、最適な背圧値の点１９ｂ、点１９ｃ、点１９ｄにおいてほぼ一致するが、点１９ａにおいて最適値より過大となってしまう。 (Equation 2)
Pb = Ps × β
The back pressure Pb at this time can be expressed by a straight line A-B in the figure. This line A-E-B substantially coincides at the points 19b, 19c, and 19d of the optimum back pressure value, but is excessively greater than the optimum value at the point 19a.

この点、本実施の形態によれば、背圧調整弁２と旋回スクロール８に設けた貫通孔１の両方で背圧を調整しているから、背圧Ｐｂが高くなったとき、背圧室１８内の流体は、より低い圧力の空間へ多く流れようとする。つまり、点Ｅでの吸込圧より低い吸込圧となる運転条件、すなわち点Ｅより左の領域では、点線で示した貫通孔１による背圧調整が支配的となる。また、点Ｅでの吸込圧より高い吸込圧となる運転条件、すなわち点Ｅより右の領域では、背圧調整弁２による背圧調整が支配的となる。図６の特性を言い換えれば、背圧調整弁２の吸込圧と背圧との動作直線（Ｃ−Ｅ−Ｄ）と、貫通孔１の吸込圧と背圧との動作直線（Ａ−Ｅ−Ｂ）が途中で交差し、かつ背圧調整弁２の動作直線の勾配が貫通孔１の動作直線の勾配より小さく形成することが特徴である。   In this respect, according to the present embodiment, since the back pressure is adjusted by both the back pressure adjusting valve 2 and the through-hole 1 provided in the orbiting scroll 8, when the back pressure Pb increases, the back pressure chamber The fluid in 18 tends to flow more into the lower pressure space. That is, in the operating condition where the suction pressure is lower than the suction pressure at the point E, that is, in the region to the left of the point E, the back pressure adjustment by the through hole 1 indicated by the dotted line is dominant. Further, in the operating condition where the suction pressure is higher than the suction pressure at the point E, that is, in the region to the right of the point E, the back pressure adjustment by the back pressure regulating valve 2 is dominant. In other words, the operation straight line (CED) between the suction pressure and the back pressure of the back pressure regulating valve 2 and the operation straight line (A-E-) between the suction pressure and the back pressure of the through hole 1 are expressed in FIG. B) intersects on the way and the gradient of the operation straight line of the back pressure regulating valve 2 is smaller than the gradient of the operation straight line of the through hole 1.

したがって、背圧調整弁２と旋回スクロール８に設けた貫通孔１の両方により背圧を調整する場合、図中の線Ａ−Ｅ−Ｄに沿って動作することになる。このとき、背圧調整弁２のバネ２ｂの定数および貫通孔１の位置を調整することにより、点１９ａ〜１９ｄまでの代表的な運転条件で、最適な背圧値とほぼ一致させることができるようになる。つまり、背圧調整の自由度が上がり、より広い運転範囲において圧縮効率の高いスクロール圧縮機を実現できる。   Accordingly, when the back pressure is adjusted by both the back pressure adjusting valve 2 and the through hole 1 provided in the orbiting scroll 8, the operation is performed along the line A-E-D in the figure. At this time, by adjusting the constant of the spring 2b of the back pressure adjusting valve 2 and the position of the through hole 1, it is possible to substantially match the optimal back pressure value under typical operating conditions from points 19a to 19d. It becomes like this. That is, the degree of freedom of back pressure adjustment is increased, and a scroll compressor with high compression efficiency can be realized in a wider operating range.

ちなみに、図６の点Ｅより右の領域では、貫通孔１が通じている圧縮室１３内の平均圧力の方が背圧室１８内の圧力より高い。したがって、貫通孔１内では、圧縮室１３から背圧室１８へ向かう流れが主流となり再膨張損失低減の効果は小さくなる。しかし、圧縮室１３から背圧室１８へ逆流した流体の分だけ、吐出圧の雰囲気であるケーシング９の底に貯留した潤滑油および潤滑油に溶け込んだ冷媒が背圧室１８に流れ込む量が減るため、圧縮効率が低下することはない。 Incidentally, in the region on the right side of the point E in FIG. 6, the average pressure in the compression chamber 13 through which the through hole 1 communicates is higher than the pressure in the back pressure chamber 18. Therefore, in the through hole 1, the flow from the compression chamber 13 toward the back pressure chamber 18 becomes the main flow, and the effect of reducing the reexpansion loss is reduced. However, the amount of the lubricating oil stored in the bottom of the casing 9 that is the atmosphere of the discharge pressure and the refrigerant dissolved in the lubricating oil flows into the back pressure chamber 18 by the amount of the fluid that flows back from the compression chamber 13 to the back pressure chamber 18. Therefore, the compression efficiency does not decrease.

以上説明したように、本実施の形態によれば、固定スクロールと旋回スクロールの引付力を調整する背圧調整に伴う、圧縮流体の再膨張による損失を低減することができる。特に、広い運転範囲において圧縮効率の高いスクロール圧縮機を実現できる。   As described above, according to the present embodiment, it is possible to reduce the loss due to re-expansion of the compressed fluid accompanying the back pressure adjustment for adjusting the attractive force of the fixed scroll and the orbiting scroll. In particular, a scroll compressor with high compression efficiency can be realized in a wide operating range.

上記実施の形態では、旋回スクロールのラップに貫通孔１を穿設する例について説明したが、本発明はこれに限らず、圧縮室と背圧室を連通させるように貫通孔を設ければよい。例えば、旋回スクロールの鏡板の部分に貫通孔を設けて背圧室と圧縮室を連通させてもよい。この場合は、貫通孔の孔径をできるだけ小さくして、流路抵抗を持たせることが望ましい。   In the above embodiment, the example in which the through-hole 1 is formed in the orbiting scroll wrap has been described. However, the present invention is not limited to this, and the through-hole may be provided so as to communicate the compression chamber and the back pressure chamber. . For example, a through hole may be provided in the end plate portion of the orbiting scroll so that the back pressure chamber and the compression chamber communicate with each other. In this case, it is desirable to make the through hole as small as possible so as to have a flow path resistance.

本発明の一実施の形態のスクロール圧縮機の全体の縦断面図である。1 is an overall longitudinal sectional view of a scroll compressor according to an embodiment of the present invention. （Ａ）は本発明の一実施の形態の旋回スクロールの平面図、（Ｂ）は（Ａ）の線Ｂ−Ｂにおける断面図である。(A) is a top view of the turning scroll of one embodiment of the present invention, (B) is a sectional view in line BB of (A). 図２の実施の形態の旋回スクロールと固定スクロールにより構成される圧縮室を示す平面図である。It is a top view which shows the compression chamber comprised by the turning scroll and fixed scroll of embodiment of FIG. 本発明の一実施の形態の固定スクロールの平面図である。It is a top view of the fixed scroll of one embodiment of the present invention. 本発明の一実施の形態の背圧調整弁の縦断面図である。It is a longitudinal cross-sectional view of the back pressure regulating valve of one embodiment of the present invention. 図１の実施の形態の背圧と吸込圧の関係を示すグラフである。It is a graph which shows the relationship between the back pressure and suction pressure of embodiment of FIG.

符号の説明Explanation of symbols

１ 貫通孔
２ 背圧調整弁
７ 固定スクロール
７ａ 鏡板
７ｂ ラップ
７ｃ 歯底
７ｅ 最外周ラップ
８ 旋回スクロール
８ａ 鏡板
８ｂ ラップ
８ｃ 歯底
１３ 圧縮室
１４ 吸入ポート
１５ 吐出ポート
１８ 背圧室 DESCRIPTION OF SYMBOLS 1 Through-hole 2 Back pressure adjustment valve 7 Fixed scroll 7a End plate 7b Wrap 7c Tooth bottom 7e Outermost lap 8 Turning scroll 8a End plate 8b Wrap 8c Tooth bottom 13 Compression chamber 14 Suction port 15 Discharge port 18 Back pressure chamber

Claims (4)

鏡板に渦巻状のラップが立設された固定スクロールと、該固定スクロールに対向して旋回可能に設けられ、前記固定スクロールのラップとの間に複数の圧縮室を形成する渦巻状のラップが立設された旋回スクロールと、前記旋回スクロールの背面に設けられ吐出圧力と吸込圧力の中間圧力が導入される背圧室と、前記固定スクロールの最外周ラップの歯先に形成された連通路を介して導入される吸込圧力または圧縮初期圧力と前記背圧室の圧力との差に応じて、前記背圧室の流体を前記連通路を介して前記吸込室または圧縮室に逃す背圧調整弁と、前記固定スクロールと前記旋回スクロールを収納する密閉容器に貯留される潤滑油を前記背圧室に流入させる潤滑油供給手段とを備え、
前記連通路に連通していない圧縮室と前記背圧室とを連通する貫通孔を前記旋回スクロールに設けてなり、前記貫通孔は、前記背圧室に面する前記旋回スクロールの鏡板から前記ラップの歯先まで貫通して形成されてなることを特徴とするスクロール圧縮機。 A fixed scroll in which a spiral wrap is erected on the end plate, and a spiral wrap which is provided so as to be pivotable facing the fixed scroll and forms a plurality of compression chambers between the fixed scroll wrap. An orbiting scroll provided, a back pressure chamber provided on the back surface of the orbiting scroll, into which an intermediate pressure between discharge pressure and suction pressure is introduced, and a communication path formed at the tooth tip of the outermost peripheral wrap of the fixed scroll. A back pressure regulating valve that releases the fluid in the back pressure chamber to the suction chamber or the compression chamber through the communication path according to the difference between the suction pressure or the compression initial pressure introduced by the pressure and the pressure in the back pressure chamber; And a lubricating oil supply means for causing the lubricating oil stored in a sealed container containing the fixed scroll and the orbiting scroll to flow into the back pressure chamber ,
The orbiting scroll is provided with a through hole that communicates the compression chamber not communicating with the communication passage and the back pressure chamber, and the through hole extends from the end plate of the orbiting scroll facing the back pressure chamber to the lap. A scroll compressor characterized in that it is formed so as to penetrate to the tooth tip. 吐出圧力と吸込圧力との中間の圧力となる背圧室の圧力によって旋回スクロールを固定スクロールに押し付けると共に前記旋回スクロールと前記固定スクロールとで複数の圧縮室を構成するスクロール圧縮機において、
吸込圧力または圧縮初期圧力と、前記背圧室の圧力と、の差に応じて前記背圧室の圧力を前記吸込圧力または前記圧縮初期圧力に逃す背圧調整弁と、前記固定スクロールと前記旋回スクロールを収納する密閉容器に貯留される潤滑油を前記背圧室に流入させる潤滑油供給手段とを備え、
前記圧縮初期圧力の圧縮室とは別の圧縮室と前記背圧室とを連通するよう、前記旋回スクロールのラップの歯先から前記旋回スクロールの前記背圧室側まで、貫通孔を形成したことを特徴とするスクロール圧縮機。 In the scroll compressor which presses the orbiting scroll against the fixed scroll by the pressure of the back pressure chamber which is an intermediate pressure between the discharge pressure and the suction pressure and constitutes a plurality of compression chambers with the orbiting scroll and the fixed scroll.
A back pressure regulating valve that releases the pressure in the back pressure chamber to the suction pressure or the compression initial pressure according to the difference between the suction pressure or the compression initial pressure and the pressure in the back pressure chamber , the fixed scroll, and the swivel Lubricating oil supply means for flowing lubricating oil stored in an airtight container for storing the scroll into the back pressure chamber ,
A through hole is formed from the tip of the orbiting scroll wrap to the back pressure chamber side of the orbiting scroll so as to communicate the compression chamber different from the compression chamber of the initial compression pressure and the back pressure chamber. Scroll compressor characterized by. 前記流体は、冷媒ガスであることを特徴とする請求項１に記載のスクロール圧縮機。 The scroll compressor according to claim 1, wherein the fluid is a refrigerant gas. 前記背圧調整弁の吸込圧と背圧との動作直線と前記貫通孔の吸込圧と背圧との動作直線が途中で交差し、背圧調整弁の動作直線の勾配が前記貫通孔の動作直線の勾配より小さいことを特徴とする請求項１又は２に記載のスクロール圧縮機。 The operation straight line between the suction pressure and back pressure of the back pressure adjustment valve intersects the operation straight line between the suction pressure and back pressure of the through hole, and the gradient of the operation straight line of the back pressure adjustment valve is the operation of the through hole. The scroll compressor according to claim 1 or 2 , wherein the scroll compressor is smaller than a linear gradient.
JP2004073092A 2004-03-15 2004-03-15 Scroll compressor Expired - Fee Related JP4519489B2 (en)

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