JP6302813B2 - Scroll compressor and refrigeration cycle apparatus using the same - Google Patents

Scroll compressor and refrigeration cycle apparatus using the same Download PDF

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JP6302813B2
JP6302813B2 JP2014200554A JP2014200554A JP6302813B2 JP 6302813 B2 JP6302813 B2 JP 6302813B2 JP 2014200554 A JP2014200554 A JP 2014200554A JP 2014200554 A JP2014200554 A JP 2014200554A JP 6302813 B2 JP6302813 B2 JP 6302813B2
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space
oil
pressure
scroll
orbiting
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JP2016070178A (en
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近野　雅嗣
雅嗣 近野
太田原　優
優 太田原
中村　聡
中村　　聡
長谷川　修士
修士 長谷川
泰典 中野
泰典 中野
坪野　勇
勇 坪野
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Hitachi Johnson Controls Air Conditioning Inc
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Hitachi Johnson Controls Air Conditioning Inc
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Priority to JP2014200554A priority Critical patent/JP6302813B2/en
Priority to CN201810866792.9A priority patent/CN109026706B/en
Priority to US15/511,323 priority patent/US20170306951A1/en
Priority to CN201580052774.1A priority patent/CN106795881B/en
Priority to PCT/JP2015/077515 priority patent/WO2016052503A1/en
Priority to CN201810865760.7A priority patent/CN108980036B/en
Publication of JP2016070178A publication Critical patent/JP2016070178A/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
    • F04C18/0253—Details concerning the base
    • F04C18/0261—Details of the ports, e.g. location, number, 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/021—Control systems for the circulation of the lubricant
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Description

本発明は、冷凍サイクルに使用されるスクロール圧縮機及びこれを用いた冷凍サイクル装置に係り、特に、旋回スクロールの背面中心部に形成された吐出圧力に近い圧力となる第１の空間と、この第1の空間よりも外周側に設けられた吐出圧力と吸込圧力との間の圧力となる第２の空間を備えるスクロール圧縮機に関する。
する。 The present invention relates to a scroll compressor used in a refrigeration cycle and a refrigeration cycle apparatus using the same, and in particular, a first space having a pressure close to a discharge pressure formed at the center of the rear surface of the orbiting scroll, and this The present invention relates to a scroll compressor including a second space which is a pressure between a discharge pressure and a suction pressure provided on the outer peripheral side of the first space.
To do.

冷凍用や空調用などの冷凍サイクル装置に使用されるスクロール圧縮機としては、特開２０１１−５８４３９号公報（特許文献１）に記載されたものなどがある。この特許文献１のものには、端板（台板、鏡板）と該端板に立設された渦巻状のラップを有する固定スクロール及び旋回スクロールと、これら固定スクロール及び旋回スクロールを互いに噛み合わせて形成される圧縮室と、前記旋回スクロールを旋回運動させるためのクランク軸と、前記旋回スクロールの背面ボス部に設けられ前記クランク軸の偏心ピン部に対し前記旋回スクロールを軸方向に移動可能でかつ回転自在に支持するための旋回軸受と、前記旋回スクロールの背面側に対向するように設けられた静止側のフレームと、このフレームに設けられ前記クランク軸を回転自在に支持する主軸受と、前記旋回スクロール背面側と前記フレームとの間をシールするシール部材と、このシール部材により区画された内周側の高圧油圧室と外周側の背圧室とを備え、前記高圧油圧室には吐出圧力にほぼ等しい圧力の潤滑油が供給されてほぼ吐出圧力に維持され、前記背圧室は吐出圧力より低い圧力に維持されるように構成したスクロール圧縮機において、前記シール部材に対向する部分の旋回スクロール背面部或いは前記フレームに小孔を設け、この小孔は前記旋回スクロールの旋回運動に伴い前記シール手段を跨いで前記高圧油圧室側と背圧室側の両方に交互に開口するようにして、高圧油圧室の油を背圧室側に供給する給油手段と、前記旋回スクロール或いは前記フレームに設けられ、前記高圧油圧室と背圧室を連通し差圧で高圧油圧室の油を背圧室側に供給する給油路とを備えたスクロール圧縮機が記載されている。   Examples of scroll compressors used in refrigeration cycle apparatuses for refrigeration and air conditioning include those described in JP 2011-58439 A (Patent Document 1). In this Patent Document 1, an end plate (base plate, end plate), a fixed scroll and a turning scroll having a spiral wrap standing on the end plate, and the fixed scroll and the turning scroll are meshed with each other. A compression chamber formed; a crankshaft for orbiting the orbiting scroll; and a rear boss portion of the orbiting scroll, the orbiting scroll being axially movable relative to an eccentric pin portion of the crankshaft; A orbiting bearing for rotatably supporting, a stationary frame provided so as to face the back side of the orbiting scroll, a main bearing provided on the frame and rotatably supporting the crankshaft, A seal member that seals between the back side of the orbiting scroll and the frame, and a high-pressure hydraulic chamber and an outer periphery on the inner periphery defined by the seal member Back pressure chamber, and the high pressure hydraulic chamber is supplied with lubricating oil having a pressure substantially equal to the discharge pressure so as to be substantially maintained at the discharge pressure, and the back pressure chamber is maintained at a pressure lower than the discharge pressure. In the scroll compressor configured as described above, a small hole is provided in the back portion of the orbiting scroll facing the seal member or the frame, and the small hole straddles the sealing means with the orbiting motion of the orbiting scroll. An oil supply means for supplying the oil in the high pressure hydraulic chamber to the back pressure chamber side so as to open alternately on both the side and the back pressure chamber side, and the orbiting scroll or the frame. There is described a scroll compressor including an oil supply passage that communicates a pressure chamber and supplies oil in a high-pressure hydraulic chamber to the back pressure chamber with a differential pressure.

また、特開２００５−１６３６５５号公報（特許文献２）には、端板（台板）とそれに立設する渦巻体（ラップ）とを有する非旋回スクロール（固定スクロール）、端板（鏡板）とそれに立設する渦巻体とを有すると共に、前記非旋回スクロールと噛み合って旋回運動をすることにより該非旋回スクロールとの間に吸込室または圧縮室を形成する旋回スクロール、該旋回スクロールに前記非旋回スクロールへの押付力を付与するための背圧室、該背圧室の圧力を維持するために該背圧室に流体を流入させるための背圧室流体流入手段、前記背圧室に流入した流体を前記吸込室または圧縮室に流出させるための背圧室流体流出手段などを備えたスクロール圧縮機が記載されている。   Japanese Patent Application Laid-Open No. 2005-163655 (Patent Document 2) discloses a non-orbiting scroll (fixed scroll) having an end plate (base plate) and a spiral body (lap) standing on the end plate (end plate), and an end plate (end plate). A orbiting scroll standing up therewith, and a revolving scroll which meshes with the non-orbiting scroll to form a suction chamber or a compression chamber between the non-orbiting scroll and the non-orbiting scroll. A back pressure chamber for applying a pressing force to the back pressure chamber, a back pressure chamber fluid inflow means for allowing fluid to flow into the back pressure chamber to maintain the pressure of the back pressure chamber, and a fluid flowing into the back pressure chamber A scroll compressor provided with a back pressure chamber fluid outflow means or the like for allowing the air to flow into the suction chamber or the compression chamber is described.

また、この特許文献２のものには、前記背圧室流体流出手段が、前記背圧室と前記吸込室または圧縮室とを繋ぐ背圧室流体流出路に、前後の差圧を制御する背圧制御弁と、絞り流路部と、前記旋回スクロール部材の旋回運動により間欠的に連通する間欠流路部とを直列に配したものが記載されている。   Further, according to this Patent Document 2, the back pressure chamber fluid outflow means controls the back pressure chamber fluid outflow path connecting the back pressure chamber and the suction chamber or the compression chamber to control the differential pressure across the back and forth. A pressure control valve, a throttle channel part, and an intermittent channel part intermittently communicating with the orbiting movement of the orbiting scroll member are described in series.

更に、特開２０１２−９２７７３号公報（特許文献３）には、鏡板（台板）とそれに立設されたスクロールラップを有する固定スクロールと、鏡板とそれに立設されたスクロールラップを有し、前記固定スクロールと噛み合わされて旋回運動を行うことによって前記固定スクロールとの間に圧縮室を形成する旋回スクロールと、前記旋回スクロールに前記固定スクロールへの引付力を与える背圧室と、前記背圧室に圧縮機吐出側の油を導入する給油路とを有するスクロール圧縮機において、前記背圧室と閉込み開始後の前記圧縮室に連通されると共に前後の差圧で開閉する背圧弁を備え、背圧室の油を圧縮室へ流出させて前記背圧室の圧力を制御する圧縮室連通路と、前記背圧室と前記圧縮室に至る吸込領域と連通し、閉込み開始後の前記圧縮室には連通しないように構成され、前記背圧室の油を前記吸込領域へ供給する吸込域連通路とを備えているものが記載されている。   Further, JP 2012-92773 A (Patent Document 3) includes a fixed scroll having an end plate (base plate) and a scroll wrap erected on the end plate, a end plate and a scroll wrap erected on the end plate, A orbiting scroll that forms a compression chamber with the fixed scroll by meshing with the fixed scroll, and a back pressure chamber that applies an attractive force to the fixed scroll to the orbiting scroll; and the back pressure A scroll compressor having an oil supply passage for introducing oil on the discharge side of the compressor into the chamber, comprising a back pressure valve that communicates with the back pressure chamber and the compression chamber after the start of closing and opens and closes by a differential pressure before and after , Communicating with the compression chamber communication passage for controlling the pressure of the back pressure chamber by allowing the oil in the back pressure chamber to flow out to the compression chamber, and the suction region leading to the back pressure chamber and the compression chamber, and Pressure It is configured not to communicate to the chamber, that the oil of the back pressure chamber and a suction zone communicating passage for supplying to said suction areas are described.

特開２０１１−５８４３９号公報JP 2011-58439 A 特開２００５−１６３６５５号公報JP 2005-163655 A 特開２０１２−９２７７３号公報JP 2012-92773 A

上記特許文献１のものでは、高圧油圧室の油を背圧室側に供給する給油手段及び給油路を備え、高圧油圧室から背圧室へ流入する油量を調整できるようにしているが、背圧室に供給された油は、その後全て吸込室に流入し、この吸込室を経由して圧縮室に流れる構成となっている。このため、吸込室で必要な給油量に圧縮室で必要な給油量も加算されて多量の高温の油が吸込室に流入することになり、吸込ガスが加熱されて加熱損失（吸込加熱損失）が大きくなってしまうことに対する配慮が為されていない。   In the thing of the said patent document 1, although it has the oil supply means and oil supply path which supply the oil of a high pressure hydraulic chamber to the back pressure chamber side, it has enabled it to adjust the oil quantity which flows in into a back pressure chamber from a high pressure hydraulic chamber, All the oil supplied to the back pressure chamber then flows into the suction chamber and flows into the compression chamber via the suction chamber. For this reason, the amount of oil required in the compression chamber is added to the amount of oil required in the suction chamber and a large amount of high-temperature oil flows into the suction chamber, and the suction gas is heated to cause a heating loss (suction heating loss). No consideration has been given to the increase in size.

また、上記特許文献２のものは、軸受部に給油された油のほとんどが背圧室に流入する構成となっており、その後背圧室の油は全て吸込室に流れる構成のため、吸込室には軸受で必要な極めて多量の油が流入することになり、上記特許文献１のものより、はるかに多くの油が吸込室に流入するため、吸込ガスが加熱されて加熱損失が更に大きくなること、圧縮室にも大量の油が供給されるため、油圧縮を引き起こす可能性があることに対する配慮が為されていない。   Moreover, the thing of the said patent document 2 becomes a structure into which most of the oil supplied to the bearing part flows in into a back pressure chamber, and since all the oil of a back pressure chamber flows into a suction chamber after that, a suction chamber A very large amount of oil required for the bearing flows into the cylinder, and much more oil flows into the suction chamber than that of Patent Document 1, so that the suction gas is heated and the heating loss is further increased. In addition, since a large amount of oil is supplied to the compression chamber, no consideration is given to the possibility of causing oil compression.

更に、上記特許文献３のものも、上記特許文献２のものと同様に、軸受部に給油された油のほとんどが背圧室に流入する構成となっている。また、この特許文献３のものでは、吸込域連通路の他に圧縮室連通路も備えることで、背圧室の油の一部を、吸込室を経由しないで直接圧縮室に供給できるため、背圧室から吸込室への給油量は、上記特許文献２のものより少なくすることはできる。しかし、軸受部に給油された油のほとんどが背圧室に流入するため、特許文献２のものより、吸込室への給油量を減少させることはできるものの、吸込室に必要とされる給油量よりはるかに多くの油が吸込室に流入することは回避することは困難である。即ち、軸受部で必要とする給油量は、吸込室や圧縮室で必要とされる給油量の例えば１０倍程度と、はるかに多いが、軸受部に供給された油のほとんどが背圧室に流入するため、吸込室への給油量も必然的に多くなることは回避できない。このため、吸込ガスが加熱されて加熱損失が大きくなることは回避することができない。また、圧縮室には背圧室から大量の油が供給され、吸込室からの油と合流するので、圧縮室への給油量が多くなって油圧縮を引き起こす可能性があることは上記特許文献２と同様であり、これらの課題に対する配慮が為されていない。   Furthermore, the thing of the said patent document 3 also becomes the structure into which most of the oil supplied to the bearing part flows into a back pressure chamber like the thing of the said patent document 2. FIG. In addition, in this Patent Document 3, by providing a compression chamber communication passage in addition to the suction region communication passage, a part of the oil in the back pressure chamber can be directly supplied to the compression chamber without going through the suction chamber. The amount of oil supplied from the back pressure chamber to the suction chamber can be made smaller than that in Patent Document 2. However, since most of the oil supplied to the bearing portion flows into the back pressure chamber, the amount of oil supplied to the suction chamber can be reduced from that of Patent Document 2, but the amount of oil required for the suction chamber is reduced. It is difficult to avoid much more oil flowing into the suction chamber. That is, the amount of oil required in the bearing portion is much larger, for example, about 10 times the amount of oil required in the suction chamber or the compression chamber, but most of the oil supplied to the bearing portion is in the back pressure chamber. Since it flows in, it cannot be avoided that the amount of oil supply to the suction chamber inevitably increases. For this reason, it cannot be avoided that the suction gas is heated and the heating loss increases. In addition, since a large amount of oil is supplied to the compression chamber from the back pressure chamber and merges with the oil from the suction chamber, the amount of oil supplied to the compression chamber may increase and cause oil compression. This is the same as 2 and no consideration is given to these issues.

本発明の目的は、軸受部への給油量、吸込室への給油量及び圧縮室への給油量のそれぞれを制御して、それぞれに適正な量の給油を実現することのできるスクロール圧縮機及びこれを用いた冷凍サイクル装置を得ることにある。   An object of the present invention is to provide a scroll compressor capable of controlling the amount of oil supplied to the bearing portion, the amount of oil supplied to the suction chamber, and the amount of oil supplied to the compression chamber, respectively, and realizing an appropriate amount of oil supply to each The object is to obtain a refrigeration cycle apparatus using this.

上記目的を達成するため、本発明は、台板に渦巻状のラップを立設した固定スクロールと、鏡板に立設した渦巻状のラップを有し前記固定スクロールと噛み合わされて旋回運動をする旋回スクロールとを備え、前記固定スクロールに対して前記旋回スクロールを旋回運動させることにより吸込室及び圧縮室を形成するように構成しているスクロール圧縮機において、前記旋回スクロールの背面中心部に形成され密閉容器底部に貯留された潤滑油が導かれて吐出圧力に近い圧力となる第１の空間と、前記旋回スクロールの背面で前記第1の空間よりも外周側に設けられ吐出圧力と吸込圧力との間の圧力となる第２の空間と、前記第１の空間内の一部の油を前記第２の空間へ漏出させる第１の油漏出路と、前記第１の空間内の大部分の油を密閉容器内の底部へ戻す油戻し通路と、前記第２の空間内の油の一部を前記吸込室へ漏出させるための第２の油漏出路と、圧縮室内の圧力と前記第２の空間内の圧力との差に応じて、前記第２の空間内の油を圧縮室に逃がすようにして前記第２の空間内の圧力を調整する第３の油漏出路とを備えることを特徴とする。   In order to achieve the above object, the present invention provides a fixed scroll having a spiral wrap standing on a base plate and a swivel having a spiral wrap standing on an end plate and meshing with the fixed scroll to make a swivel motion. A scroll compressor configured to form a suction chamber and a compression chamber by orbiting the orbiting scroll with respect to the fixed scroll. A first space in which the lubricating oil stored in the bottom of the container is guided to a pressure close to the discharge pressure, and a discharge pressure and a suction pressure provided on the outer periphery side of the first space on the back of the orbiting scroll. A second space serving as a pressure between the first space, a first oil leakage path for leaking a part of oil in the first space to the second space, and most of the oil in the first space. The sealed container An oil return passage for returning to the bottom of the inside, a second oil leakage path for leaking a part of the oil in the second space to the suction chamber, a pressure in the compression chamber, and a pressure in the second space And a third oil leakage path for adjusting the pressure in the second space so as to allow the oil in the second space to escape to the compression chamber in accordance with the difference from the pressure.

本発明の他の特徴は、上記のように構成されたスクロール圧縮機を用いて構成した冷凍空調用の冷凍サイクル装置にある。   Another feature of the present invention resides in a refrigeration cycle apparatus for refrigeration and air conditioning constructed using the scroll compressor constructed as described above.

本発明によれば、軸受部への給油量、吸込室への給油量及び圧縮室への給油量のそれぞれを制御して、それぞれに適正な量の給油を実現することのできるスクロール圧縮機及びこれを用いた冷凍サイクル装置を得ることができる効果がある。   According to the present invention, a scroll compressor capable of controlling the amount of oil supplied to the bearing portion, the amount of oil supplied to the suction chamber, and the amount of oil supplied to the compression chamber, respectively, and realizing an appropriate amount of oil supply, and There exists an effect which can obtain the refrigerating cycle device using this.

本発明のスクロール圧縮機の実施例１を示す縦断面図。BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal sectional view showing a first embodiment of a scroll compressor according to the present invention. 図１に示す固定スクロールと旋回スクロールとの噛み合っている状態を示す図で、図１のII−II方向から見た図。It is a figure which shows the state which the fixed scroll and turning scroll shown in FIG. 1 mesh, and the figure seen from the II-II direction of FIG. 図１に示す旋回スクロールを上方から見た斜視図。The perspective view which looked at the turning scroll shown in FIG. 1 from upper direction. 図１に示すスクロール圧縮機における背圧弁周辺の拡大断面図。The expanded sectional view of the back pressure valve periphery in the scroll compressor shown in FIG. 旋回スクロールの他の例を説明する図で、図２に相当する斜視図。FIG. 9 is a diagram for explaining another example of the orbiting scroll, and is a perspective view corresponding to FIG. 2. 本発明のスクロール圧縮機の実施例２を説明する図で、図４に相当する図。FIG. 5 is a diagram for explaining Example 2 of the scroll compressor according to the present invention and corresponding to FIG. 4. 本発明の実施例３を説明する図で、スクロール圧縮機を用いた冷凍サイクル装置の例を示す冷凍サイクル構成図。It is a figure explaining Example 3 of this invention, and is the refrigerating-cycle block diagram which shows the example of the refrigerating-cycle apparatus using a scroll compressor.

以下、本発明の具体的実施例を、図面を用いて説明する。なお、各図において、同一符号を付した部分は同一或いは相当する部分を示している。   Hereinafter, specific embodiments of the present invention will be described with reference to the drawings. Note that, in each drawing, the portions denoted by the same reference numerals indicate the same or corresponding portions.

本発明のスクロール圧縮機の実施例１を図１〜図５を用いて説明する。図１は本発明のスクロール圧縮機の実施例１を示す縦断面図、図２は図１に示す固定スクロールと旋回スクロールとの噛み合っている状態を示す図で、図１のII−II方向から見た図、図３は図１に示す旋回スクロールを上方から見た斜視図、図４は図１に示すスクロール圧縮機における背圧弁周辺の拡大断面図、図５は旋回スクロールの他の例を説明する図で、図３に相当する斜視図である。   A scroll compressor according to a first embodiment of the present invention will be described with reference to FIGS. 1 is a longitudinal sectional view showing a first embodiment of a scroll compressor according to the present invention, and FIG. 2 is a view showing a state in which a fixed scroll and a turning scroll shown in FIG. 1 are engaged with each other, from the direction II-II in FIG. FIG. 3 is a perspective view of the orbiting scroll shown in FIG. 1 as viewed from above, FIG. 4 is an enlarged cross-sectional view of the periphery of the back pressure valve in the scroll compressor shown in FIG. 1, and FIG. It is a figure to explain and is a perspective view equivalent to FIG.

まず、図１により、本実施例のスクロール圧縮機の全体構成を説明する。
スクロール圧縮機１は、ケース（密閉容器）９内に、圧縮機構部２及びモータ部１６などを収容して構成されている。
前記圧縮機構部２では、フレーム１７に固定された固定スクロール７に、旋回スクロール８が噛み合わされて、圧縮室１３が形成され、前記モータ部１６の回転により、クランクシャフト（回転軸）１０を介して、前記旋回スクロール８を旋回運動させることにより、前記圧縮室１３の容積を減少させて圧縮動作を行う。 First, the overall configuration of the scroll compressor of this embodiment will be described with reference to FIG.
The scroll compressor 1 is configured by housing a compression mechanism section 2 and a motor section 16 in a case (sealed container) 9.
In the compression mechanism section 2, the orbiting scroll 8 is meshed with the fixed scroll 7 fixed to the frame 17 to form a compression chamber 13, and the rotation of the motor section 16 causes the crankshaft (rotary shaft) 10 to pass through. Thus, the revolving motion of the orbiting scroll 8 reduces the volume of the compression chamber 13 and performs the compressing operation.

この圧縮動作に伴って、作動流体が吸込ポート１４から吸込室２０（図３参照）へ吸込まれ、吸込まれた作動流体は圧縮室１３での圧縮行程を経て、吐出ポート１５からケース９内の吐出空間５４に吐出される。この吐出空間５４に吐出された作動流体は、前記固定スクロール７の外周と前記フレーム１７の外周に形成された通路（図示せず）を通って、モータ室５２に流れ、その後吐出パイプ６からケース９外に吐出されるように構成されている。   Along with this compression operation, the working fluid is sucked into the suction chamber 20 (see FIG. 3) from the suction port 14, and the sucked working fluid passes through the compression stroke in the compression chamber 13 and is discharged from the discharge port 15 into the case 9. It is discharged into the discharge space 54. The working fluid discharged into the discharge space 54 flows into the motor chamber 52 through a passage (not shown) formed in the outer periphery of the fixed scroll 7 and the outer periphery of the frame 17, and then from the discharge pipe 6 to the case. 9 is configured to be discharged outside.

前記固定スクロール７は、円板状の台板７ａ、この台板７ａに渦巻状に立設されたラップ７ｂ、前記台板７ａの外周側に位置し、前記ラップ７ｂの先端面とほぼ同じ高さの鏡板面７ｅを有してラップ７ｂを囲むように筒状に設けられた支持部７ｄを備えている。前記ラップ７ｂが立設された台板７ａの表面は、ラップ７ｂの間にあるため、歯底７ｃと呼ばれる。   The fixed scroll 7 is a disk-shaped base plate 7a, a wrap 7b erected on the base plate 7a in a spiral shape, and is positioned on the outer peripheral side of the base plate 7a, and is substantially the same height as the front end surface of the wrap 7b. And a support portion 7d provided in a cylindrical shape so as to surround the wrap 7b. Since the surface of the base plate 7a on which the wrap 7b is erected is located between the wraps 7b, it is called a tooth bottom 7c.

前記鏡板面７ｅは、固定スクロール７の支持部７ｄが、旋回スクロール８の鏡板８ａと接する摺動面となっている。固定スクロール７は、前記支持部７ｄをボルト等により前記フレーム１７に固定しており、固定スクロール７と一体に結合された前記フレーム１７は溶接等の固定手段により前記ケース９に固定されている。   The end plate surface 7 e is a sliding surface where the support portion 7 d of the fixed scroll 7 is in contact with the end plate 8 a of the orbiting scroll 8. The fixed scroll 7 has the support portion 7d fixed to the frame 17 with bolts or the like, and the frame 17 integrally coupled with the fixed scroll 7 is fixed to the case 9 by fixing means such as welding.

前記旋回スクロール８は、固定スクロール７に対向して配置され、固定スクロール７のラップ７ｂと旋回スクロール８のラップ８ｂとが噛み合わされて、フレーム１７内に旋回可能に設けられている。この旋回スクロール８は、円板状の鏡板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、及び前記鏡板８ａの背面中央に設けられた旋回ボス部（ボス部）８ｄを有する。また、前記鏡板８ａの外周部の前記固定スクロール７と接する表面は、旋回スクロール８の鏡板面８ｅとなっている。   The orbiting scroll 8 is disposed so as to face the fixed scroll 7, and the wrap 7 b of the fixed scroll 7 and the wrap 8 b of the orbiting scroll 8 are engaged with each other so that the orbiting scroll 8 is provided inside the frame 17. The orbiting scroll 8 includes a spiral wrap 8b erected from a tooth bottom 8c, which is the surface of a disc-shaped end plate 8a, and an orbiting boss portion (boss portion) 8d provided at the center of the rear surface of the end plate 8a. Have. Further, the surface of the outer peripheral portion of the end plate 8 a that contacts the fixed scroll 7 is the end plate surface 8 e of the orbiting scroll 8.

前記旋回スクロール８のラップ８ｂの先端部（ラップ歯先）は前記固定スクロール７の歯底７ｃと微小すき間をもって相対するように構成されている。同様に、固定スクロール７のラップ７ｂの先端部（ラップ歯先）も前記旋回スクロール８の歯底８ｃと微小すき間をもって相対するように構成されている。   The tip end portion (wrap tooth tip) of the wrap 8b of the orbiting scroll 8 is configured to face the tooth bottom 7c of the fixed scroll 7 with a small gap. Similarly, the tip end portion (wrap tooth tip) of the wrap 7b of the fixed scroll 7 is also configured to face the tooth bottom 8c of the orbiting scroll 8 with a minute gap.

前記圧縮機構部２及びモータ部１６等を収容している密閉容器構造の前記ケース９の底部には、潤滑油（冷凍機油）を溜める油溜り５３が設けられている。前記モータ部１６は回転子１６ａと固定子１６ｂにより構成され、前記回転子１６ａにはクランクシャフト１０が一体に固定されている。このクランクシャフト１０は前記フレーム１７に主軸受５を介して回転自在に支持され、固定スクロール７の中心軸線と同軸となっている。   An oil sump 53 for storing lubricating oil (refrigerating machine oil) is provided at the bottom of the case 9 having a sealed container structure that accommodates the compression mechanism unit 2, the motor unit 16, and the like. The motor unit 16 includes a rotor 16a and a stator 16b, and the crankshaft 10 is integrally fixed to the rotor 16a. The crankshaft 10 is rotatably supported by the frame 17 via the main bearing 5 and is coaxial with the central axis of the fixed scroll 7.

前記クランクシャフト１０の先端には偏心したクランク部１０ａが設けられており、このクランク部１０ａは、前記旋回スクロール８の旋回ボス部８ｄに設けられた旋回軸受１１に挿入され、前記旋回スクロール８はクランクシャフト１０の回転に伴い旋回可能に構成されている。   An eccentric crank portion 10 a is provided at the tip of the crankshaft 10, and this crank portion 10 a is inserted into the orbiting bearing 11 provided in the orbiting boss portion 8 d of the orbiting scroll 8. The crankshaft 10 is configured to be able to turn as the crankshaft 10 rotates.

前記旋回スクロール８の中心軸線は、前記固定スクロール７の中心軸線に対して所定距離だけ偏心した状態となる。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に対し、周方向に所定角度（一般には１８０度）だけずらして重ね合わせられている。
１２は、前記旋回スクロール８を前記固定スクロール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オルダムリングである。 The center axis of the orbiting scroll 8 is decentered by a predetermined distance with respect to the center 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 (generally 180 degrees) in the circumferential direction.
Reference numeral 12 denotes an Oldham ring for relatively turning the orbiting scroll 8 with respect to the fixed scroll 7 while restraining the orbiting scroll 8 from rotating.

図２は前記固定スクロール７と旋回スクロール８との噛み合い状態を説明する図で、図１のII−II方向から見た図であるため、旋回スクロール８については、旋回スクロールラップ８ｂが断面で示され、旋回スクロール８の鏡板８ａの外周に相当する部分は二点鎖線（想像線）で示している。   FIG. 2 is a diagram for explaining the meshing state of the fixed scroll 7 and the orbiting scroll 8, and is a view seen from the II-II direction of FIG. 1, so that the orbiting scroll wrap 8b is shown in cross section for the orbiting scroll 8. A portion corresponding to the outer periphery of the end plate 8a of the orbiting scroll 8 is indicated by a two-dot chain line (imaginary line).

この図２に示すように、固定スクロールラップ７ｂと旋回スクロールラップ８ｂ間には三日月状の複数の圧縮室１３（旋回内線側圧縮室１３ａ、旋回外線側圧縮室１３ｂ）が形成され、旋回スクロール８を旋回運動させると、各圧縮室１３は中央部の方向に移動するに従い、連続的にその容積が縮小されていく。
２０は吸込室で、流体を吸入している途中の空間である。この吸込室２０は、旋回スクロール８の旋回運動の位相が進んで、流体の閉じ込みを完了した時点から圧縮室１３となる。 As shown in FIG. 2, a plurality of crescent-shaped compression chambers 13 (orbiting inner line side compression chambers 13a and orbiting outer line side compression chambers 13b) are formed between the fixed scroll wrap 7b and the orbiting scroll wrap 8b. When each of the compression chambers 13 is swung, the volume of each compression chamber 13 is continuously reduced as the compression chambers 13 move toward the center.
Reference numeral 20 denotes a suction chamber, which is a space in the middle of sucking fluid. The suction chamber 20 becomes the compression chamber 13 when the phase of the orbiting motion of the orbiting scroll 8 advances and the closing of the fluid is completed.

前記吸込ポート１４は、図１及び図２に示すように、固定スクロール７に設けられている。この吸込ポート１４は、前記吸込室２０と連通するように、固定スクロール７の台板７ａの外周側に穿設されている。
前記吐出ポート１５は、最内周側の圧縮室１３と連通するように、前記固定スクロール７の台板７ａの渦巻中心付近に穿設されている。 The suction port 14 is provided in the fixed scroll 7 as shown in FIGS. 1 and 2. The suction port 14 is formed on the outer peripheral side of the base plate 7 a of the fixed scroll 7 so as to communicate with the suction chamber 20.
The discharge port 15 is formed near the spiral center of the base plate 7a of the fixed scroll 7 so as to communicate with the compression chamber 13 on the innermost peripheral side.

図１に示す前記モータ部１６により前記クランクシャフト１０を回転させると、前記旋回スクロール８は、前記固定スクロール７の中心軸線を中心に、所定の旋回半径をもって旋回運動する。これにより、前記吸込ポート１４から吸込まれた作動流体、例えば冷凍サイクルを循環する冷媒ガス（以下、単に流体ともいう）を前記各圧縮室１３内で順次圧縮し、圧縮された作動流体は前記吐出ポート１５から前記吐出空間５４に吐出され、上述したように、前記吐出パイプ６から、圧縮機外の例えば冷凍サイクルに供給される。   When the crankshaft 10 is rotated by the motor unit 16 shown in FIG. 1, the orbiting scroll 8 orbits with a predetermined orbiting radius around the central axis of the fixed scroll 7. As a result, the working fluid sucked from the suction port 14, for example, refrigerant gas (hereinafter also simply referred to as fluid) circulating in the refrigeration cycle, is sequentially compressed in each compression chamber 13, and the compressed working fluid is discharged from the discharge chamber. The gas is discharged from the port 15 into the discharge space 54 and, as described above, supplied from the discharge pipe 6 to, for example, a refrigeration cycle outside the compressor.

前記クランクシャフト１０の下端には、容積型または遠心式の給油ポンプ２１が設けられており、前記クランクシャフト１０の回転と共に、前記給油ポンプ２１も回転し、前記ケース９底部の油溜り５３に溜められた潤滑油を、給油ポンプケース２２の潤滑油吸込口２２ａから吸入して、前記給油ポンプ２１の吐出口２１ａから吐出する。吐出された潤滑油は、前記クランクシャフト１０内に軸方向に形成されている貫通穴（給油穴）３を通って、前記クランク部１０ａの上端の旋回ボス部８ｄ内空間へ送られる。   A positive displacement or centrifugal oil pump 21 is provided at the lower end of the crankshaft 10, and as the crankshaft 10 rotates, the oil pump 21 also rotates and accumulates in an oil sump 53 at the bottom of the case 9. The obtained lubricating oil is sucked from the lubricating oil suction port 22 a of the oil supply pump case 22 and discharged from the discharge port 21 a of the oil supply pump 21. The discharged lubricating oil passes through a through hole (oil supply hole) 3 formed in the axial direction in the crankshaft 10 and is sent to the space in the turning boss portion 8d at the upper end of the crank portion 10a.

なお、前記貫通穴３を流れる潤滑油の一部は、前記クランクシャフト１０に設けられている横穴２４を介して副軸受２３に送られ、該副軸受２３を潤滑後、ケース９底部の前記油溜り５３に戻る。前記貫通穴３を流れるその他の大部分の潤滑油は、前記クランク部１０ａの上端の前記旋回ボス部空間に達し、前記クランク部１０ａの外周面に設けた油溝５７を通って前記旋回軸受１１を潤滑する。この潤滑油は、その後、前記旋回軸受１１の下部に設けた前記主軸受５を潤滑した後、排油穴２６ａ及び排油パイプ２６ｂで構成されている油戻し通路２６を通ってケース９底部の前記油溜り５３に戻される。   A part of the lubricating oil flowing through the through hole 3 is sent to the auxiliary bearing 23 through a lateral hole 24 provided in the crankshaft 10, and after lubricating the auxiliary bearing 23, the oil at the bottom of the case 9 is supplied. Return to pool 53. Most of the other lubricating oil flowing through the through-hole 3 reaches the turning boss part space at the upper end of the crank part 10a, passes through the oil groove 57 provided on the outer peripheral surface of the crank part 10a, and the turning bearing 11. Lubricate. This lubricating oil then lubricates the main bearing 5 provided at the lower part of the slewing bearing 11, and then passes through an oil return passage 26 constituted by an oil drain hole 26a and an oil drain pipe 26b, so that the bottom of the case 9 is The oil sump 53 is returned.

ここで、前記油溝５７と前記旋回軸受１１などで形成される前記旋回ボス部内空間と、前記主軸受５を収める空間（フレーム１７、クランクシャフト１０、フレームシール５６、旋回ボス部８ｄに設けられたつば部３４及びシール部材３２で形成された空間）を合わせて第１の空間３３と呼ぶことにする。この第１の空間３３は吐出圧力に近い圧力を有する空間である。   Here, the inner space of the swivel boss part formed by the oil groove 57 and the swivel bearing 11 and the space (the frame 17, the crankshaft 10, the frame seal 56, the swivel boss part 8d for housing the main bearing 5 are provided. The space formed by the collar portion 34 and the seal member 32) will be collectively referred to as a first space 33. The first space 33 is a space having a pressure close to the discharge pressure.

前記主軸受５及び前記旋回軸受１１の潤滑のために前記第１の空間３３に流入した潤滑油の大部分は、前記排油穴２６ａ及び前記排油パイプ２６ｂ（油戻し通路）を通って、ケース９底部の前記油溜り５３に戻る。また、前記潤滑油の一部は、前記オルダムリング１２の潤滑、前記固定スクロール７と旋回スクロール８との摺動部の潤滑、及び前記各ラップ７ｂ，８ｂの先端すき間などのシール（密閉）に必要な量が、前記シール部材３２の上端面と、前記旋回ボス部８ｄの前記つば部３４端面との間に設けられた第１の油漏出路を介して、前記第1の空間３３よりも外周側に設けられ吐出圧力と吸込圧力との間の圧力となる第２の空間である背圧室１８に流入する。   Most of the lubricating oil flowing into the first space 33 for lubricating the main bearing 5 and the slewing bearing 11 passes through the oil drain hole 26a and the oil drain pipe 26b (oil return passage). Return to the oil sump 53 at the bottom of the case 9. Further, a part of the lubricating oil is used for sealing (sealing) such as lubrication of the Oldham ring 12, lubrication of the sliding portion between the fixed scroll 7 and the orbiting scroll 8, and gaps between the tips of the laps 7 b and 8 b. The required amount is larger than that of the first space 33 via the first oil leakage path provided between the upper end surface of the seal member 32 and the end surface of the flange portion 34 of the turning boss portion 8d. It flows into the back pressure chamber 18 which is a second space provided on the outer peripheral side and serving as a pressure between the discharge pressure and the suction pressure.

前記シール部材３２は、前記フレーム１７の前記つば部３４と対向する面に設けられた円環溝３１に、波状バネ（図示せず）と共に設けられており、吐出圧力となっている前記第１の空間３３と、吸込圧力と吐出圧力の中間の圧力となっている前記背圧室（第２の空間）１８とを仕切っている。   The seal member 32 is provided with a wave spring (not shown) in an annular groove 31 provided on a surface of the frame 17 facing the flange portion 34, and serves as a discharge pressure. , And the back pressure chamber (second space) 18 which is an intermediate pressure between the suction pressure and the discharge pressure.

前記第１の油漏出路は、例えば、旋回ボス部８ｄの前記つば部３４に設けられた一つまたは複数の半径方向に長いスリット６０（溝）と、前記シール部材３２とにより構成され、前記スリット６０は、前記旋回スクロール８の旋回運動により間欠的に、前記シール部材３２を跨ぐように配置されることで、間欠的に前記第１の空間３３と前記背圧室１８を連通するように構成されている。   The first oil leakage path includes, for example, one or a plurality of radially long slits 60 (grooves) provided in the flange portion 34 of the turning boss portion 8d, and the seal member 32. The slit 60 is intermittently disposed so as to straddle the seal member 32 by the orbiting motion of the orbiting scroll 8 so as to intermittently communicate the first space 33 and the back pressure chamber 18. It is configured.

これにより、前記第１の空間３３と前記背圧室１８との圧力差により、前記第１の空間３３から前記背圧室１８へ、微小すき間である前記スリット６０を介して、油を流入させることができる。
なお、前記スリット６０の配置は、旋回スクロール８の旋回運動に伴い間欠的に前記シール部材３２を跨ぐ構成とするものには限られず、常にシール部材３２を跨ぐようにしてもよい。 As a result, due to the pressure difference between the first space 33 and the back pressure chamber 18, oil flows from the first space 33 to the back pressure chamber 18 through the slit 60, which is a minute gap. be able to.
Note that the arrangement of the slit 60 is not limited to a configuration in which the seal member 32 is intermittently straddled with the orbiting motion of the orbiting scroll 8, and the seal member 32 may be always straddled.

また、前記スリット６０の代わりに、旋回ボス部の前記つば部３４に、１つまたは複数個、即ち１以上の油溜めとなる穴（例えば円形の溝）を設け、この穴が、旋回スクロール８の旋回運動に伴って前記シール部材３２を跨いだ円運動を行うように構成する。これにより、前記穴は、前記第１の空間３３と前記背圧室１８との間を移動し、前記第１の空間３３の潤滑油を該穴に溜め、前記背圧室１８に間欠的に移送して排出することができ、第１の空間３３内の油を背圧室１８に供給することができる。このように前記第１の油漏出路を構成しても良い。   Further, instead of the slit 60, one or a plurality of holes, for example, one or more oil reservoirs (for example, circular grooves) are provided in the collar portion 34 of the orbiting boss portion. A circular motion straddling the seal member 32 is performed in accordance with the swiveling motion. As a result, the hole moves between the first space 33 and the back pressure chamber 18, the lubricating oil in the first space 33 is accumulated in the hole, and intermittently enters the back pressure chamber 18. The oil can be transferred and discharged, and the oil in the first space 33 can be supplied to the back pressure chamber 18. In this way, the first oil leakage path may be configured.

本実施例では、前記背圧室１８に流入した潤滑油の一部は、後述する第２の油漏出路を介して前記吸込室２０に流入するように構成されており、ラップ摺動面やラップ先端すき間などを潤滑すると共に、圧縮室間などのシールにも利用される。   In this embodiment, a part of the lubricating oil that has flowed into the back pressure chamber 18 is configured to flow into the suction chamber 20 via a second oil leakage path to be described later. In addition to lubricating the gap between the wrap tips, it is also used for sealing between the compression chambers.

また、前記背圧室１８に流入した潤滑油の残りは、後述する第３の油漏出路を介して前記圧縮室１３に流入するように構成されており、圧縮室のラップ摺動面やラップ先端すき間などを潤滑すると共に、圧縮室間などのシールに利用される。   The remainder of the lubricating oil that has flowed into the back pressure chamber 18 is configured to flow into the compression chamber 13 via a third oil leakage path, which will be described later. It is used for sealing the gap between the tip and the like, and for sealing between the compression chambers.

このように、本実施例では、前記第１の空間３３から前記第２の空間（背圧室）１８へ、前記第１の油漏出路を介して、ラップ摺動面やラップ先端すき間などの潤滑や、圧縮室間などのシールに必要な量だけ潤滑油を漏出させ、残りの潤滑油は、各軸受部を潤滑後、前記排油穴２６ａ及び排油パイプ２６ｂを介して油溜り５３に戻すことができる。従って、本実施例では、各軸受部の潤滑に必要な給油量と、背圧室１８への給油量を独立に制御することができる。従って、背圧室１８への給油量を必要最小限にすることができる。   As described above, in this embodiment, a lap sliding surface, a lap tip clearance, and the like are passed from the first space 33 to the second space (back pressure chamber) 18 through the first oil leakage path. Lubricating oil is leaked in an amount necessary for lubrication and sealing between the compression chambers, and the remaining lubricating oil is lubricated to the oil sump 53 through the oil draining hole 26a and the oil draining pipe 26b after lubricating the bearings. Can be returned. Therefore, in this embodiment, the amount of oil required for lubrication of each bearing portion and the amount of oil supplied to the back pressure chamber 18 can be controlled independently. Therefore, the amount of oil supplied to the back pressure chamber 18 can be minimized.

また、前記背圧室１８へ流入した潤滑油は、前記第２の油漏出路を介して吸込室２０に必要な給油量だけ供給することができ、残りの潤滑油は前記第３の油漏出路を介して圧縮室１３に供給する。従って、吸込室２０及び圧縮室１３への給油量をそれぞれ必要最小限にすることができるから、前記吸込室２０での吸込加熱損失を最小限にすることができ、また前記圧縮室１３での油の過剰供給による油圧縮や加熱損失などを防止できるから、高効率で信頼性の高いスクロール圧縮機を実現することができる。   Further, the lubricating oil flowing into the back pressure chamber 18 can be supplied to the suction chamber 20 through the second oil leakage path, and the remaining lubricating oil can be supplied to the third oil leakage. It supplies to the compression chamber 13 through a path. Therefore, since the amount of oil supplied to the suction chamber 20 and the compression chamber 13 can be minimized, the suction heating loss in the suction chamber 20 can be minimized, and in the compression chamber 13 Since it is possible to prevent oil compression and heating loss due to excessive supply of oil, a highly efficient and highly reliable scroll compressor can be realized.

次に、前記第２の油漏出路の構成について、図２及び図３を用いて説明する。
６４は、図３に示すように、旋回スクロール８の鏡板面８ｅに設けられ油溜めとなる油穴（溝）で、この油穴６４は、図２に示すように、旋回スクロール８の旋回運動に伴い、図２に示す軌跡６５を描いて、背圧室（第２の空間）１８と、吸込室２０に連通した溝部６６とに間欠的に連通する。 Next, the configuration of the second oil leakage path will be described with reference to FIGS. 2 and 3.
As shown in FIG. 3, 64 is an oil hole (groove) provided on the end plate surface 8e of the orbiting scroll 8 and serving as an oil reservoir. This oil hole 64 is an orbiting motion of the orbiting scroll 8 as shown in FIG. Accordingly, the locus 65 shown in FIG. 2 is drawn, and the back pressure chamber (second space) 18 and the groove 66 communicating with the suction chamber 20 are intermittently communicated.

前記油穴６４が背圧室１８に連通している状態では、背圧室１８内(圧力は吐出圧力と吸込圧力の中間の圧力)の油が前記油穴６４内に溜められる。また、前記油穴６４が、旋回スクロール８の旋回運動に伴い、前記溝部６６（圧力は吸込圧力）に連通すると、前記油穴６４内の油が、圧力差により前記溝部６６を経由して前記吸込室２０に導入される。この作用を繰り返すことにより、前記背圧室１８内の油は、順次吸込室２０に移送される。前記油穴６４の容積や個数を調整することにより、前記背圧室１８から前記吸込室２０への給油量を任意に調整することが可能となる。   In a state where the oil hole 64 communicates with the back pressure chamber 18, the oil in the back pressure chamber 18 (the pressure is an intermediate pressure between the discharge pressure and the suction pressure) is accumulated in the oil hole 64. Further, when the oil hole 64 communicates with the groove 66 (pressure is a suction pressure) as the orbiting scroll 8 rotates, the oil in the oil hole 64 passes through the groove 66 due to a pressure difference. It is introduced into the suction chamber 20. By repeating this action, the oil in the back pressure chamber 18 is sequentially transferred to the suction chamber 20. By adjusting the volume and number of the oil holes 64, the amount of oil supplied from the back pressure chamber 18 to the suction chamber 20 can be arbitrarily adjusted.

次に、前記第３の油漏出路の構成について、図１、図２及び図４を用いて説明する。
まず、前記背圧室（第２の空間）１８の機能について説明する。スクロール圧縮機１では、その圧縮作用により、固定スクロール７と旋回スクロール８を互いに引離そうとする軸方向の力（引き離し力）が発生する。この軸方向の力により、前記両スクロールが引き離される、いわゆる旋回スクロール８の離脱現象が発生すると、圧縮室１３の密閉性が悪化し、圧縮機効率を低下させる。 Next, the configuration of the third oil leakage path will be described with reference to FIGS. 1, 2, and 4.
First, the function of the back pressure chamber (second space) 18 will be described. In the scroll compressor 1, an axial force (separation force) that causes the fixed scroll 7 and the orbiting scroll 8 to be separated from each other is generated by the compression action. When the so-called orbiting scroll 8 separation phenomenon occurs in which the two scrolls are separated by this axial force, the sealing performance of the compression chamber 13 deteriorates and the compressor efficiency is lowered.

そこで、旋回スクロール８の鏡板８ａ背面側に、吐出圧力と吸込圧力の間の圧力となる背圧室１８を設け、この背圧室１８の圧力（背圧）により、前記引き離し力を打ち消すと共に、旋回スクロール８を固定スクロール７に押付けるようにしている。このときの押付力が大きすぎると、旋回スクロール８の鏡板面８ｅと固定スクロール７の鏡板面７ｅとの摺動損失が増大し、圧縮機効率が低下する。   Therefore, a back pressure chamber 18 serving as a pressure between the discharge pressure and the suction pressure is provided on the back side of the end plate 8a of the orbiting scroll 8, and the pulling force is canceled by the pressure (back pressure) of the back pressure chamber 18, The orbiting scroll 8 is pressed against the fixed scroll 7. If the pressing force at this time is too large, the sliding loss between the end plate surface 8e of the orbiting scroll 8 and the end plate surface 7e of the fixed scroll 7 increases, and the compressor efficiency decreases.

つまり、前記背圧には最適な値が存在し、小さすぎると圧縮室の密閉性が悪化して熱流体損失が増大し、大きすぎると摺動損失が増大する。従って、背圧を最適な値に維持することが、圧縮機の高性能化、高信頼性化において重要である。   In other words, there is an optimum value for the back pressure. If the back pressure is too small, the sealing performance of the compression chamber deteriorates and the thermal fluid loss increases, and if it is too large, the sliding loss increases. Therefore, maintaining the back pressure at an optimum value is important in improving the performance and reliability of the compressor.

この最適な背圧値を得るため、本実施例のスクロール圧縮機では、図１に示すように、前記背圧室１８の背圧を調整するための背圧弁６１を有する前記第３の油漏出路（圧縮室連通路）が前記固定スクロール７の支持部７ｄに備えられている。
図１における背圧弁６１周辺の構成を示す拡大図である図４を用いて、前記第３の油漏出路の構成を詳細に説明する。 In order to obtain this optimum back pressure value, in the scroll compressor of this embodiment, as shown in FIG. 1, the third oil leakage having a back pressure valve 61 for adjusting the back pressure in the back pressure chamber 18 is provided. A path (compression chamber communication path) is provided in the support portion 7 d of the fixed scroll 7.
The configuration of the third oil leakage path will be described in detail with reference to FIG. 4 which is an enlarged view showing the configuration around the back pressure valve 61 in FIG.

前記第３の油漏出路（圧縮室連通路）は、前記背圧室１８と前記背圧弁６１を連通する背圧弁流入路（背圧室１８と通じている空間）６２ａ、前記背圧弁６１と前記圧縮室１３を連通する背圧弁流出路（圧縮室１３に通じている空間）６２ｃ、及び前記背圧弁６１を収容している空間６２ｂにより構成されている。前記背圧弁６１は、前記背圧弁流入路６２ａと前記背圧弁流出路６２ｃを仕切るようにバルブ６１ａが配置されている。このバルブ６１ａは、ストッパ６１ｃに固定されたばね６１ｂにより、前記背圧弁流入路６２ａの開口部に押付けられるように設けられている。   The third oil leakage path (compression chamber communication path) includes a back pressure valve inflow path (a space communicating with the back pressure chamber 18) 62a communicating the back pressure chamber 18 and the back pressure valve 61, and the back pressure valve 61. A back pressure valve outflow passage (a space communicating with the compression chamber 13) 62c communicating with the compression chamber 13 and a space 62b accommodating the back pressure valve 61 are configured. The back pressure valve 61 is provided with a valve 61a so as to partition the back pressure valve inflow passage 62a and the back pressure valve outflow passage 62c. The valve 61a is provided to be pressed against the opening of the back pressure valve inflow passage 62a by a spring 61b fixed to the stopper 61c.

前記バルブ６１ａは、前記背圧弁流入路６２ａ内の圧力、即ち背圧が、前記背圧弁流出路６２ｃを介して導入される前記空間６２ｂ内の圧力、即ち圧縮室の圧力と、ばね６１ｂの押付力に対応する圧力の合計よりも高くなった場合に、上方へ移動して、前記背圧弁流入路６２ａと前記背圧弁流出路６２ｃとを連通させる。つまり、前記背圧弁６１は、背圧室１８内の圧力がある値よりも高くなった場合に、該背圧室１８内の流体を前記圧縮室１３に逃がし、前記背圧室１８の背圧を適正値に調整するものである。   The valve 61a is configured such that the pressure in the back pressure valve inflow passage 62a, that is, the back pressure is introduced through the back pressure valve outflow passage 62c, that is, the pressure in the space 62b, that is, the pressure in the compression chamber, and the spring 61b. When the pressure becomes higher than the total pressure corresponding to the force, the back pressure valve inflow path 62a and the back pressure valve outflow path 62c are communicated with each other by moving upward. That is, when the pressure in the back pressure chamber 18 becomes higher than a certain value, the back pressure valve 61 allows the fluid in the back pressure chamber 18 to escape to the compression chamber 13, and the back pressure in the back pressure chamber 18. Is adjusted to an appropriate value.

前記圧縮室１３へ流入した油は、ラップ摺動面やラップ先端すき間などを潤滑すると共に、圧縮室間などのシールに利用され、その後、前記吐出ポート１５から吐出空間５４に吐出される。この吐出された油の一部は、例えば冷媒ガスと共に前記吐出パイプ６から冷凍サイクルへ吐出され、残りはケース９内で冷媒ガスと分離されてケース底の前記油溜り５３に貯留される。   The oil that has flowed into the compression chamber 13 lubricates the lap sliding surface and the gap between the wrap tips, and is used for sealing between the compression chambers, and is then discharged from the discharge port 15 into the discharge space 54. A part of the discharged oil is discharged together with the refrigerant gas from the discharge pipe 6 to the refrigeration cycle, for example, and the rest is separated from the refrigerant gas in the case 9 and stored in the oil reservoir 53 at the bottom of the case.

上記特許文献２や特許文献３に記載の従来のスクロール圧縮機では、前記第１の空間、即ち軸受部へ給油された潤滑油のほぼ全てが背圧室１８に流入し、その後吸込室２０及び圧縮室１３へと流れる。このため、吸込室２０への給油量も圧縮室１３への給油量も過多になってしまい、高温の潤滑油により冷媒が加熱されて膨張し、吸込加熱損失が増大すると共に、吸込室２０に吸引できる冷媒量も減少するため体積効率が低下する。また、圧縮室１３へは軸受部へ給油された潤滑油のほぼ全てが流入するため、加熱損失の増大と油圧縮による圧縮動力の増大が生じる。   In the conventional scroll compressor described in Patent Document 2 and Patent Document 3, almost all of the lubricating oil supplied to the first space, that is, the bearing portion, flows into the back pressure chamber 18, and then the suction chamber 20 and It flows to the compression chamber 13. For this reason, the amount of oil supplied to the suction chamber 20 and the amount of oil supplied to the compression chamber 13 become excessive, the refrigerant is heated and expanded by the high-temperature lubricating oil, the suction heating loss increases, and the suction chamber 20 Since the amount of refrigerant that can be sucked also decreases, volumetric efficiency decreases. In addition, since almost all of the lubricating oil supplied to the bearing portion flows into the compression chamber 13, an increase in heating loss and an increase in compression power due to oil compression occur.

一方、上記特許文献１のものでは背圧室１８への給油量を独立に制御できるが、吸込室での吸込加熱損失を抑制するために、背圧室１８へ流入する潤滑油量を抑えると、圧縮室１３へ十分な給油ができず、圧縮室１３における油による密閉効果が低下するため、漏れ損失が増大する。   On the other hand, in the thing of the said patent document 1, although the amount of oil supply to the back pressure chamber 18 can be controlled independently, in order to suppress the suction heating loss in a suction chamber, if the amount of lubricating oil which flows into the back pressure chamber 18 is suppressed, Since sufficient oil cannot be supplied to the compression chamber 13 and the sealing effect of the oil in the compression chamber 13 is reduced, leakage loss increases.

即ち、従来のものでは、吸込室２０及び圧縮機１３にそれぞれ適切な量の潤滑油を供給することはできなかった。
これに対し、本実施例は、前記第１の油漏出路により、各軸受部への給油量と背圧室への給油量を独立に制御できるようにし、また第２の油漏出路により背圧室１８から吸込室２０に給油する給油量を独立に制御し、更に背圧室１８から背圧弁６１を介して、吸込過程を完了した後の圧縮室１３に給油する第３の油漏出路を備えているので、各軸受部、吸込室２０及び圧縮室１３へのそれぞれの給油量を適切に調整できるようにしたものである。 That is, in the prior art, it has been impossible to supply appropriate amounts of lubricating oil to the suction chamber 20 and the compressor 13 respectively.
In contrast, in the present embodiment, the amount of oil supplied to each bearing portion and the amount of oil supplied to the back pressure chamber can be independently controlled by the first oil leakage path, and the backside by the second oil leakage path. A third oil leakage path for independently controlling the amount of oil supplied from the pressure chamber 18 to the suction chamber 20 and for supplying oil from the back pressure chamber 18 to the compression chamber 13 after completing the suction process via the back pressure valve 61. Therefore, the amount of oil supplied to each bearing portion, the suction chamber 20 and the compression chamber 13 can be adjusted appropriately.

なお、本実施例において、前記背圧弁流出路６２ｃは、吸込過程を完了して圧縮を開始した後の圧縮室１３に連通している。即ち、この圧縮室１３は、吸込過程を完了した後の圧縮途中の圧縮室であり、吸込室２０とは隔離された圧縮室である。また、前記背圧弁流出路６２ｃは、図２に示すように、旋回スクロールの旋回運動により旋回外線室１３ｂと旋回内線室１３ａの両方に交互に連通する位置としている。
なお、図４に示す６３は止め栓であり、背圧弁流出路６２ｃを設けるために形成された横穴の端部を密閉して塞ぐためのものである。 In the present embodiment, the back pressure valve outflow passage 62c communicates with the compression chamber 13 after the suction process is completed and compression is started. That is, the compression chamber 13 is a compression chamber in the middle of compression after completing the suction process, and is a compression chamber isolated from the suction chamber 20. Further, as shown in FIG. 2, the back pressure valve outflow passage 62c is in a position where it alternately communicates with both the turning outer line chamber 13b and the turning inner line chamber 13a by the turning motion of the turning scroll.
In addition, 63 shown in FIG. 4 is a stopcock for sealing and closing the edge part of the horizontal hole formed in order to provide the back pressure valve outflow path 62c.

本実施例では、前記背圧弁６１を有する第３の油漏出路を設けているので、背圧室１８内の油を、吸込室２０を経由することなく、前記背圧弁６１を介して圧縮室１３に直接供給することができる。この圧縮室１３への給油量は、前記第１の油漏出路による前記第１の空間３３から前記背圧室１８への給油量と、前記第２の油漏出路による前記背圧室１８から吸込室２０への給油量との差分となる。即ち、前記背圧室１８へは前記第１の油漏出手段を介して第１の空間３３から油が供給されるが、その油のうち第２の油漏出路により決定される量だけが吸込室に導入され、残りの油は圧縮室１３に導入される。   In the present embodiment, since the third oil leakage path having the back pressure valve 61 is provided, the oil in the back pressure chamber 18 is compressed through the back pressure valve 61 without passing through the suction chamber 20. 13 can be supplied directly. The amount of oil supplied to the compression chamber 13 is determined from the amount of oil supplied from the first space 33 to the back pressure chamber 18 by the first oil leakage path and from the back pressure chamber 18 by the second oil leakage path. This is the difference from the amount of oil supplied to the suction chamber 20. That is, oil is supplied from the first space 33 to the back pressure chamber 18 via the first oil leakage means, but only the amount determined by the second oil leakage path is sucked in the oil. The remaining oil is introduced into the compression chamber 13.

従って、前記第１の油漏出路と第２の油漏出路のそれぞれの給油量を調整することにより、吸込室への給油量と圧縮室への給油量をそれぞれ適切な量に制御することが可能となる。   Therefore, the amount of oil supplied to the suction chamber and the amount of oil supplied to the compression chamber can be controlled to appropriate amounts by adjusting the amount of oil supplied to each of the first oil leakage path and the second oil leakage path. It becomes possible.

一般に、圧縮室１３のシールに必要な給油量は吸込室のシールに必要な給油量より多くなるので、例えば上記特許文献１のものでは、第１の油漏出路での給油量を、圧縮室のシールに必要な給油量に設定した場合、吸込室２０では給油過多となり吸込加熱損失が増大する。逆に、第１の油漏出路での給油量を、吸込室２０のシールに必要なだけの少ない給油量に設定した場合には、圧縮室では給油不足となり油による密閉効果が低下して漏れ損失が増大する。   In general, the amount of oil required for sealing the compression chamber 13 is larger than the amount of oil required for sealing the suction chamber. For example, in the above-mentioned Patent Document 1, the amount of oil supplied in the first oil leakage path is set to the compression chamber. When the amount of oil required for the seal is set, the suction chamber 20 becomes excessively oiled and the suction heating loss increases. Conversely, if the oil supply amount in the first oil leakage path is set to a low oil supply amount that is necessary for sealing the suction chamber 20, the compression chamber will become insufficiently oiled and the sealing effect by the oil will be reduced and leakage will occur. Loss increases.

これに対し、本実施例では、吸込室と圧縮室のそれぞれに適量の油を供給することが可能なため、上記特許文献１のものに比べ、吸込加熱損失や漏れ損失を低減することができる。
更に、背圧弁流出路６２ｃは、旋回スクロールの旋回運動により、前記旋回外線室１３ｂと前記旋回内線室１３ａの両方に交互に連通する位置に形成されているため、両方の圧縮室に油を供給することができ、何れかの圧縮室１３で給油が不足する不具合を回避することができる。 On the other hand, in this embodiment, since it is possible to supply an appropriate amount of oil to each of the suction chamber and the compression chamber, it is possible to reduce the suction heating loss and the leakage loss as compared with the above-mentioned Patent Document 1. .
Further, since the back pressure valve outflow passage 62c is formed at a position alternately communicating with both the swirling outer chamber 13b and the swirling inner chamber 13a by the swirling motion of the orbiting scroll, oil is supplied to both the compression chambers. It is possible to avoid the problem of insufficient oil supply in any one of the compression chambers 13.

また、第１の油漏出路による給油量が、第２の油漏出路による給油量より多くなるように各給油量を設定することで、第１の油漏出路と第２の油漏出路の給油量の差分を圧縮室１３に供給できるから、圧縮室１３への給油量を確実に確保することができる。   Moreover, by setting each oil supply amount so that the amount of oil supplied by the first oil leak path is larger than the amount of oil supplied by the second oil leak path, the first oil leak path and the second oil leak path Since the difference in the amount of oil supply can be supplied to the compression chamber 13, the amount of oil supply to the compression chamber 13 can be reliably ensured.

更に、作動流体として、高温になりやすい、断熱指数が１．０９より大きい冷媒、例えばＲ３２などを用いるスクロール圧縮機に本実施例を適用すれば、吸込加熱損失をより低減でき、より効率の高いスクロール圧縮機を得ることができる。   Furthermore, if the present embodiment is applied to a scroll compressor that uses a refrigerant that tends to be high temperature and has a heat insulation index greater than 1.09, such as R32, as the working fluid, the suction heating loss can be further reduced, and the efficiency is higher. A scroll compressor can be obtained.

なお、上述した実施例では、図３に示したように、前記第２の油漏出路を、旋回スクロール８の鏡板面８ｅに円形の油穴（溝）６４を設けて構成した例を説明したが、これに限るものではない。即ち、図５に示すように、前記油穴６４に代えて、深さの浅いスリット（溝）６７とし、このスリット６７が常時または間欠的に、背圧室１８と、吸込室２０に連通した溝部６６とに連通するようにして、圧力差により、背圧室１８の油を吸込室２０に導入するように構成しても良い。この場合でも、前記スリットの深さ、幅、長さ或いは個数などを調整することにより給油量を制御できる。   In the above-described embodiment, as shown in FIG. 3, the second oil leakage path has been described by providing a circular oil hole (groove) 64 on the end plate surface 8 e of the orbiting scroll 8. However, it is not limited to this. That is, as shown in FIG. 5, instead of the oil hole 64, a shallow slit (groove) 67 is formed, and the slit 67 communicates with the back pressure chamber 18 and the suction chamber 20 constantly or intermittently. The oil in the back pressure chamber 18 may be introduced into the suction chamber 20 by a pressure difference so as to communicate with the groove 66. Even in this case, the amount of oil supply can be controlled by adjusting the depth, width, length, or number of the slits.

本発明のスクロール圧縮機の実施例２を、図６を用いて説明する。図６は、上述した図４に相当する図であり、この図６において、上述した図１〜図５と同一符号を付した部分は同一或いは相当する部分を示している。   A scroll compressor according to a second embodiment of the present invention will be described with reference to FIG. FIG. 6 is a view corresponding to FIG. 4 described above, and in FIG. 6, the portions denoted by the same reference numerals as those of FIGS. 1 to 5 described above indicate the same or corresponding portions.

本実施例２においても、上述した実施例１と同様に、前記第１の油漏出路により、各軸受部への給油量と背圧室への給油量を独立に制御できるようにし、また第２の油漏出路により背圧室１８から吸込室２０に給油する給油量を独立に制御できるようにしている。しかし、本実施例２では、図４に示したような、背圧室１８から背圧弁６１を介して圧縮室１３に給油するような第３の油漏出路は備えていない。本実施例２における前記第３の油漏出路は、固定スクロール７の支持部７ｄには備えられておらず、図６に示すように、旋回スクロール８の鏡板８ａに形成した背圧孔６８により構成されている。   In the second embodiment, similarly to the first embodiment, the first oil leakage path allows the oil supply amount to each bearing portion and the oil supply amount to the back pressure chamber to be independently controlled. The amount of oil supplied from the back pressure chamber 18 to the suction chamber 20 can be controlled independently by two oil leakage paths. However, the second embodiment does not include a third oil leakage path for supplying oil from the back pressure chamber 18 to the compression chamber 13 via the back pressure valve 61 as shown in FIG. In the second embodiment, the third oil leakage path is not provided in the support portion 7d of the fixed scroll 7, but by a back pressure hole 68 formed in the end plate 8a of the orbiting scroll 8, as shown in FIG. It is configured.

前記背圧孔６８は、背圧室（第２の空間）１８と、吸込過程を完了して圧縮を開始した後の圧縮室１３とを連通するように前記旋回スクロール鏡板８ａに設けた構成にしている。即ち、前記背圧孔６８は、吸込室２０とは隔離された圧縮室１３にのみ連通する位置に設けられている。この背圧孔６８により、前記背圧室１８内の圧力を、圧縮室１３内の平均圧力に近い値に維持することができる。   The back pressure hole 68 is provided in the orbiting scroll end plate 8a so as to communicate the back pressure chamber (second space) 18 with the compression chamber 13 after completing the suction process and starting the compression. ing. That is, the back pressure hole 68 is provided at a position communicating only with the compression chamber 13 isolated from the suction chamber 20. With the back pressure hole 68, the pressure in the back pressure chamber 18 can be maintained at a value close to the average pressure in the compression chamber 13.

上述したように、前記第１の油漏出路、前記第２の油漏出路、及び前記背圧孔６８（第３の油漏出路）を備えることにより、上記実施例１と同様に、各軸受部、吸込室２０及び圧縮室１３へのそれぞれの給油量を適切に調整することが可能となる。   As described above, each bearing is provided with the first oil leakage path, the second oil leakage path, and the back pressure hole 68 (third oil leakage path) in the same manner as in the first embodiment. It is possible to appropriately adjust the amount of oil supplied to each part, the suction chamber 20 and the compression chamber 13.

以上述べた本発明の各実施例によれば、軸受部への給油量、吸込室への給油量及び圧縮室への給油量のそれぞれを制御して、それぞれに適正な量の給油を実現して、損失の小さい高効率なスクロール圧縮機を実現することができる。なお、前記第１〜第３の油漏出路から漏出する油（潤滑油）には、一般に冷媒も含まれているが、本発明では油に冷媒が含まれているものも油として説明している。   According to each embodiment of the present invention described above, an appropriate amount of oil is realized by controlling the amount of oil supplied to the bearing portion, the amount of oil supplied to the suction chamber, and the amount of oil supplied to the compression chamber. Thus, a highly efficient scroll compressor with low loss can be realized. The oil (lubricating oil) leaking from the first to third oil leakage paths generally includes a refrigerant. However, in the present invention, the oil containing the refrigerant is also described as oil. Yes.

本発明の実施例３を図７により説明する。図７は、上述した本発明のスクロール圧縮機を用いた冷凍空調用の冷凍サイクル装置の一例を示す冷凍サイクル構成図である。   A third embodiment of the present invention will be described with reference to FIG. FIG. 7 is a refrigeration cycle configuration diagram showing an example of a refrigeration cycle apparatus for refrigeration and air conditioning using the above-described scroll compressor of the present invention.

本実施例では、冷凍サイクル装置としての空気調和機に適用した場合の例を図７により説明する。図７において、１はスクロール圧縮機、４３は四方弁、４０は室外側熱交換器（冷房運転時は凝縮器、暖房運転時は蒸発器となる）、４１は電子膨張弁などで構成された膨張弁、４２は室内側熱交換器（冷房運転時は蒸発器、暖房運転時は凝縮器となる）であり、これらの機器は冷媒配管により順次接続されて、空気調和機の冷凍サイクルが構成されている。前記スクロール圧縮機１は、本実施例では、上記各実施例に記載されたスクロール圧縮機の何れかが使用されている。   In this embodiment, an example in which the present invention is applied to an air conditioner as a refrigeration cycle apparatus will be described with reference to FIG. In FIG. 7, 1 is a scroll compressor, 43 is a four-way valve, 40 is an outdoor heat exchanger (condenser during cooling operation, evaporator during heating operation), and 41 is an electronic expansion valve. An expansion valve 42 is an indoor heat exchanger (an evaporator during cooling operation and a condenser during heating operation), and these devices are sequentially connected by refrigerant piping to form a refrigeration cycle of the air conditioner. Has been. In the present embodiment, any one of the scroll compressors described in the above embodiments is used as the scroll compressor 1.

この図７に示すような空気調和機に、上述した本発明の何れかの実施例に記載のスクロール圧縮機を組み合わせることにより、空気調和機の運転効率を大幅に向上することができ、空気調和機の通年エネルギー消費効率（ＡＰＦ）を大幅に向上でき、年間を通じて消費電力量が小さく且つ運転範囲の広く、使い勝手の良い空気調和機（冷凍サイクル装置）を得ることができる。   By combining the air conditioner as shown in FIG. 7 with the scroll compressor described in any of the above-described embodiments of the present invention, the operating efficiency of the air conditioner can be significantly improved. The year-round energy consumption efficiency (APF) of the machine can be greatly improved, and an air conditioner (refrigeration cycle apparatus) that is small in power consumption, has a wide operation range, and is easy to use can be obtained.

なお、本実施例３では、室外側熱交換器４０が１台、室内側熱交換器４２が１台の空気調和機に適用した場合について説明したが、前記室内側熱交換器４２が複数台のマルチ型の空気調和機などにも同様に適用でき、更に冷房専用の空気調和機や冷凍機などの冷凍サイクル装置にも同様に適用することができる。   In the third embodiment, the case where the outdoor heat exchanger 40 and the indoor heat exchanger 42 are applied to one air conditioner has been described, but a plurality of the indoor heat exchangers 42 are provided. The present invention can be similarly applied to a multi-type air conditioner, and can also be applied to a refrigeration cycle apparatus such as a dedicated air conditioner or a refrigerator.

以上説明したように、本発明の各実施例によれば、軸受部への給油量、背圧室への給油量、吸込室への給油量、圧縮室への給油量を、それぞれに必要な量だけの適正な給油量にすることできるので、効率の高いスクロール圧縮機及びこれを用いた冷凍空調用の冷凍サイクル装置を得ることができる。   As described above, according to each embodiment of the present invention, the amount of oil supplied to the bearing portion, the amount of oil supplied to the back pressure chamber, the amount of oil supplied to the suction chamber, and the amount of oil supplied to the compression chamber are required. Since it is possible to obtain an appropriate amount of oil supply only by the amount, a highly efficient scroll compressor and a refrigeration cycle apparatus for refrigeration and air conditioning using the scroll compressor can be obtained.

なお、本発明は上記した実施例に限定されるものではなく、様々な変形例が含まれる。また、上記した実施例は本発明を分かり易く説明するために詳細に説明したものであり、必ずしも説明した全ての構成を備えるものに限定されるものではない。更に、各実施例の構成の一部について、他の構成の追加・削除・置換をすることが可能である。   In addition, this invention is not limited to an above-described Example, Various modifications are included. The above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described. Furthermore, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

１：スクロール圧縮機、２：圧縮機構部、
３：貫通穴（給油穴）、５：主軸受、６：吐出パイプ、
７：固定スクロール、７ａ：台板、７ｂ：ラップ、７ｃ：歯底、
７ｄ：支持部、７ｅ：鏡板面、
８：旋回スクロール、８ａ：鏡板、８ｂ：ラップ、８ｃ：歯底、
８ｄ：旋回ボス部（ボス部）、８ｅ：鏡板面、
９：ケース（密閉容器）、
１０：クランクシャフト（回転軸）、１０ａ：クランク部、
１１：旋回軸受、１２：オルダムリング、
１３：圧縮室、１３ａ：旋回内線側圧縮室、１３ｂ：旋回外線側圧縮室、
１４：吸込ポート、１５：吐出ポート、
１６：モータ部、１６ａ：回転子、１６ｂ：固定子、
１７：フレーム、
１８：背圧室、２０：吸込室、
２１：給油ポンプ、２１ａ：給油ポンプ吐出口、
２２：給油ポンプケース、２２ａ：潤滑油吸込口、
２３：副軸受、２４：横穴、
２６：油戻し通路（２６ａ：排油穴、２６ｂ：排油パイプ）、
３１：円環溝、３２：シール部材、３３：第１の空間、３４：つば部、
４０：室外側熱交換器、４１：膨張弁、４２：室内側熱交換器、４３：四方弁、
５２：モータ室、５３：油溜り、５４：吐出空間、
５６：フレームシール、５７：油溝、６０：スリット（溝）、
６１：背圧弁、６１ａ：バルブ、６１ｂ：ばね、６１ｃ：ストッパ、
６２ａ：背圧弁流入路、６２ｂ：空間、６２ｃ：背圧弁流出路、
６３：止め栓、６４：油穴（溝）、６５：油穴の軌跡、
６６：溝部、６７：スリット（溝）、６８：背圧孔。 1: scroll compressor, 2: compression mechanism,
3: through hole (oil supply hole), 5: main bearing, 6: discharge pipe,
7: fixed scroll, 7a: base plate, 7b: wrap, 7c: tooth bottom,
7d: support part, 7e: end plate surface,
8: Orbiting scroll, 8a: End plate, 8b: Wrap, 8c: Tooth base,
8d: turning boss part (boss part), 8e: end plate surface,
9: Case (sealed container),
10: Crankshaft (rotary shaft), 10a: Crank part,
11: Slewing bearing, 12: Oldham ring,
13: compression chamber, 13a: swirl extension side compression chamber, 13b: swirl extension line side compression chamber,
14: Suction port, 15: Discharge port,
16: Motor part, 16a: Rotor, 16b: Stator,
17: Frame,
18: Back pressure chamber, 20: Suction chamber,
21: Oil pump, 21a: Oil pump discharge port,
22: Oil supply pump case, 22a: Lubricating oil suction port,
23: secondary bearing, 24: side hole,
26: oil return passage (26a: oil drain hole, 26b: oil drain pipe),
31: annular groove, 32: seal member, 33: first space, 34: collar part,
40: outdoor heat exchanger, 41: expansion valve, 42: indoor heat exchanger, 43: four-way valve,
52: motor chamber, 53: oil sump, 54: discharge space,
56: Frame seal, 57: Oil groove, 60: Slit (groove),
61: Back pressure valve, 61a: Valve, 61b: Spring, 61c: Stopper,
62a: back pressure valve inflow passage, 62b: space, 62c: back pressure valve outflow passage,
63: Stopcock, 64: Oil hole (groove), 65: Trace of oil hole,
66: groove part, 67: slit (groove), 68: back pressure hole.

Claims (11)

台板に渦巻状のラップを立設した固定スクロールと、鏡板に立設した渦巻状のラップを有し前記固定スクロールと噛み合わされて旋回運動をする旋回スクロールとを備え、前記固定スクロールに対して前記旋回スクロールを旋回運動させることにより吸込室及び圧縮室を形成するように構成しているスクロール圧縮機において、
前記旋回スクロールの背面中心部に形成され密閉容器底部に貯留された潤滑油が導かれて吐出圧力に近い圧力となる第１の空間と、
前記旋回スクロールの背面で前記第1の空間よりも外周側に設けられ吐出圧力と吸込圧力との間の圧力となる第２の空間と、
前記第１の空間内の一部の油を前記第２の空間へ漏出させる第１の油漏出路と、
前記第１の空間内の大部分の油を密閉容器内の底部へ戻す油戻し通路と、
前記第２の空間内の油の一部を前記吸込室へ漏出させるための第２の油漏出路と、
圧縮室内の圧力と前記第２の空間内の圧力との差に応じて、前記第２の空間内の油を圧縮室に逃がすようにして前記第２の空間内の圧力を調整する第３の油漏出路とを備え、
前記第３の油漏出路は、前記固定スクロールに設けられ、圧縮室内の圧力と前記第２の空間内の圧力との差に応じて開閉する背圧弁を備え、前記第２の空間内の油を圧縮室に逃がすようにして前記第２の空間内の圧力を調整する構成としてい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 a base plate, and a orbiting scroll having a spiral wrap that is erected in an end plate and meshing with the fixed scroll to make a turning motion. In a scroll compressor configured to form a suction chamber and a compression chamber by orbiting the orbiting scroll,
A first space formed at the center of the back of the orbiting scroll and stored at the bottom of the hermetic container and led to a pressure close to the discharge pressure;
A second space provided on the back side of the orbiting scroll on the outer peripheral side of the first space and serving as a pressure between the discharge pressure and the suction pressure;
A first oil leakage path for leaking a part of the oil in the first space to the second space;
An oil return passage for returning most of the oil in the first space to the bottom in the sealed container;
A second oil leakage path for leaking part of the oil in the second space to the suction chamber;
According to the difference between the pressure in the compression chamber and the pressure in the second space, the pressure in the second space is adjusted so as to release oil in the second space to the compression chamber. An oil leakage path ,
The third oil leakage path is provided in the fixed scroll and includes a back pressure valve that opens and closes according to a difference between the pressure in the compression chamber and the pressure in the second space, and the oil in the second space A scroll compressor characterized in that the pressure in the second space is adjusted so as to escape to the compression chamber . 請求項１に記載のスクロール圧縮機において、前記第３の油漏出路は、前記第２の空間と前記背圧弁とを連通させる背圧弁流入路と、前記圧縮室と前記背圧弁とを連通させる背圧弁流出路とを備え、前記背圧弁流出路は吸込過程を完了して圧縮を開始した後の圧縮室へ連通させるように構成していることを特徴とするスクロール圧縮機。 2. The scroll compressor according to claim 1 , wherein the third oil leakage path communicates the back pressure valve inflow path for communicating the second space and the back pressure valve, and the compression chamber and the back pressure valve. And a back pressure valve outflow path, wherein the back pressure valve outflow path is configured to communicate with a compression chamber after completing a suction process and starting compression. 台板に渦巻状のラップを立設した固定スクロールと、鏡板に立設した渦巻状のラップを有し前記固定スクロールと噛み合わされて旋回運動をする旋回スクロールとを備え、前記固定スクロールに対して前記旋回スクロールを旋回運動させることにより吸込室及び圧縮室を形成するように構成しているスクロール圧縮機において、
前記旋回スクロールの背面中心部に形成され密閉容器底部に貯留された潤滑油が導かれて吐出圧力に近い圧力となる第１の空間と、
前記旋回スクロールの背面で前記第1の空間よりも外周側に設けられ吐出圧力と吸込圧力との間の圧力となる第２の空間と、
前記第１の空間内の一部の油を前記第２の空間へ漏出させる第１の油漏出路と、
前記第１の空間内の大部分の油を密閉容器内の底部へ戻す油戻し通路と、
前記第２の空間内の油の一部を前記吸込室へ漏出させるための第２の油漏出路と、
圧縮室内の圧力と前記第２の空間内の圧力との差に応じて、前記第２の空間内の油を圧縮室に逃がすようにして前記第２の空間内の圧力を調整する第３の油漏出路とを備え、
前記第３の油漏出路は、前記旋回スクロールに設けられ、圧縮室内の圧力と前記第２の空間内の圧力との差に応じて、前記第２の空間内の流体を圧縮室に逃がす背圧孔で構成され、前記第２の空間内の流体を圧縮室に逃がすことで前記第２の空間内の圧力を調整するようにしてい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 a base plate, and a orbiting scroll having a spiral wrap that is erected in an end plate and meshing with the fixed scroll to make a turning motion. In a scroll compressor configured to form a suction chamber and a compression chamber by orbiting the orbiting scroll,
A first space formed at the center of the back of the orbiting scroll and stored at the bottom of the hermetic container and led to a pressure close to the discharge pressure;
A second space provided on the back side of the orbiting scroll on the outer peripheral side of the first space and serving as a pressure between the discharge pressure and the suction pressure;
A first oil leakage path for leaking a part of the oil in the first space to the second space;
An oil return passage for returning most of the oil in the first space to the bottom in the sealed container;
A second oil leakage path for leaking part of the oil in the second space to the suction chamber;
According to the difference between the pressure in the compression chamber and the pressure in the second space, the pressure in the second space is adjusted so as to release oil in the second space to the compression chamber. An oil leakage path,
The third oil leakage path is provided in the orbiting scroll, and causes the fluid in the second space to escape to the compression chamber according to the difference between the pressure in the compression chamber and the pressure in the second space. A scroll compressor comprising pressure holes, wherein the pressure in the second space is adjusted by allowing the fluid in the second space to escape to the compression chamber. 請求項３に記載のスクロール圧縮機において、前記背圧孔は、吸込過程を完了して圧縮を開始した後の圧縮室と前記第２の空間とを連通させるように構成していることを特徴とするスクロール圧縮機。 4. The scroll compressor according to claim 3 , wherein the back pressure hole is configured to communicate the compression chamber and the second space after completing the suction process and starting the compression. Scroll compressor. 台板に渦巻状のラップを立設した固定スクロールと、鏡板に立設した渦巻状のラップを有し前記固定スクロールと噛み合わされて旋回運動をする旋回スクロールとを備え、前記固定スクロールに対して前記旋回スクロールを旋回運動させることにより吸込室及び圧縮室を形成するように構成しているスクロール圧縮機において、
前記旋回スクロールの背面中心部に形成され密閉容器底部に貯留された潤滑油が導かれて吐出圧力に近い圧力となる第１の空間と、
前記旋回スクロールの背面で前記第1の空間よりも外周側に設けられ吐出圧力と吸込圧力との間の圧力となる第２の空間と、
前記第１の空間内の一部の油を前記第２の空間へ漏出させる第１の油漏出路と、
前記第１の空間内の大部分の油を密閉容器内の底部へ戻す油戻し通路と、
前記第２の空間内の油の一部を前記吸込室へ漏出させるための第２の油漏出路と、
圧縮室内の圧力と前記第２の空間内の圧力との差に応じて、前記第２の空間内の油を圧縮室に逃がすようにして前記第２の空間内の圧力を調整する第３の油漏出路とを備え、
前記第３の油漏出路は、旋回外線側圧縮室と旋回内線側圧縮室の両方に連通する位置に開口してい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 a base plate, and a orbiting scroll having a spiral wrap that is erected in an end plate and meshing with the fixed scroll to make a turning motion. In a scroll compressor configured to form a suction chamber and a compression chamber by orbiting the orbiting scroll,
A first space formed at the center of the back of the orbiting scroll and stored at the bottom of the hermetic container and led to a pressure close to the discharge pressure;
A second space provided on the back side of the orbiting scroll on the outer peripheral side of the first space and serving as a pressure between the discharge pressure and the suction pressure;
A first oil leakage path for leaking a part of the oil in the first space to the second space;
An oil return passage for returning most of the oil in the first space to the bottom in the sealed container;
A second oil leakage path for leaking part of the oil in the second space to the suction chamber;
According to the difference between the pressure in the compression chamber and the pressure in the second space, the pressure in the second space is adjusted so as to release oil in the second space to the compression chamber. An oil leakage path,
The scroll compressor, wherein the third oil leakage path is open at a position communicating with both the turning outer line side compression chamber and the turning inner line side compression chamber. 台板に渦巻状のラップを立設した固定スクロールと、鏡板に立設した渦巻状のラップを有し前記固定スクロールと噛み合わされて旋回運動をする旋回スクロールとを備え、前記固定スクロールに対して前記旋回スクロールを旋回運動させることにより吸込室及び圧縮室を形成するように構成しているスクロール圧縮機において、
前記旋回スクロールの背面中心部に形成され密閉容器底部に貯留された潤滑油が導かれて吐出圧力に近い圧力となる第１の空間と、
前記旋回スクロールの背面で前記第1の空間よりも外周側に設けられ吐出圧力と吸込圧力との間の圧力となる第２の空間と、
前記第１の空間内の一部の油を前記第２の空間へ漏出させる第１の油漏出路と、
前記第１の空間内の大部分の油を密閉容器内の底部へ戻す油戻し通路と、
前記第２の空間内の油の一部を前記吸込室へ漏出させるための第２の油漏出路と、
圧縮室内の圧力と前記第２の空間内の圧力との差に応じて、前記第２の空間内の油を圧縮室に逃がすようにして前記第２の空間内の圧力を調整する第３の油漏出路とを備え、
前記旋回スクロールの背面側には回転軸と連結するための旋回ボス部が設けられ、この旋回ボス部には前記第１の空間の少なくとも一部が形成されると共に、この旋回ボス部端面側に、前記第１の空間から前記第２の空間へ必要最小限の油を漏出させるための前記第１の油漏出路が形成されてい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 a base plate, and a orbiting scroll having a spiral wrap that is erected in an end plate and meshing with the fixed scroll to make a turning motion. In a scroll compressor configured to form a suction chamber and a compression chamber by orbiting the orbiting scroll,
A first space formed at the center of the back of the orbiting scroll and stored at the bottom of the hermetic container and led to a pressure close to the discharge pressure;
A second space provided on the back side of the orbiting scroll on the outer peripheral side of the first space and serving as a pressure between the discharge pressure and the suction pressure;
A first oil leakage path for leaking a part of the oil in the first space to the second space;
An oil return passage for returning most of the oil in the first space to the bottom in the sealed container;
A second oil leakage path for leaking part of the oil in the second space to the suction chamber;
According to the difference between the pressure in the compression chamber and the pressure in the second space, the pressure in the second space is adjusted so as to release oil in the second space to the compression chamber. An oil leakage path,
On the back side of the orbiting scroll, there is provided a orbiting boss portion for connecting to the rotating shaft, and at least a part of the first space is formed on the orbiting boss portion, and on the end surface side of the orbiting boss portion. The scroll compressor is characterized in that the first oil leakage path for leaking a minimum amount of oil from the first space to the second space is formed. 請求項６に記載のスクロール圧縮機において、前記第２の空間は、前記固定スクロールと、該固定スクロールを取り付けているフレームと、前記旋回スクロールとで形成され、
前記旋回ボス部の前記第１の空間と前記第２の空間とは旋回ボス部端面側に設けたシール部材で区切られ、
前記第１の油漏出路は、前記旋回ボス部端面側に設けられた前記シール部材と、前記旋回スクロールの旋回運動により前記第１空間内の油を、前記シール部材を介して前記第２空間に間欠的に供給するように形成された溝により構成されていることを特徴とするスクロール圧縮機。 The scroll compressor according to claim 6 , wherein the second space is formed by the fixed scroll, a frame to which the fixed scroll is attached, and the orbiting scroll.
The first space and the second space of the turning boss part are separated by a seal member provided on the end face side of the turning boss part,
The first oil leakage path includes the seal member provided on the end surface side of the orbiting boss portion, and the oil in the first space by the orbiting motion of the orbiting scroll, and the second space via the seal member. A scroll compressor comprising a groove formed so as to be supplied intermittently. 請求項７に記載のスクロール圧縮機において、前記第１の油漏出路を構成する前記溝は、前記旋回ボス部端面に形成されたスリット或いは１以上の穴で構成されていることを特徴とするスクロール圧縮機。 8. The scroll compressor according to claim 7 , wherein the groove constituting the first oil leakage path is configured by a slit or one or more holes formed in an end surface of the turning boss portion. Scroll compressor. 台板に渦巻状のラップを立設した固定スクロールと、鏡板に立設した渦巻状のラップを有し前記固定スクロールと噛み合わされて旋回運動をする旋回スクロールとを備え、前記固定スクロールに対して前記旋回スクロールを旋回運動させることにより吸込室及び圧縮室を形成するように構成しているスクロール圧縮機において、
前記旋回スクロールの背面中心部に形成され密閉容器底部に貯留された潤滑油が導かれて吐出圧力に近い圧力となる第１の空間と、
前記旋回スクロールの背面で前記第1の空間よりも外周側に設けられ吐出圧力と吸込圧力との間の圧力となる第２の空間と、
前記第１の空間内の一部の油を前記第２の空間へ漏出させる第１の油漏出路と、
前記第１の空間内の大部分の油を密閉容器内の底部へ戻す油戻し通路と、
前記第２の空間内の油の一部を前記吸込室へ漏出させるための第２の油漏出路と、
圧縮室内の圧力と前記第２の空間内の圧力との差に応じて、前記第２の空間内の油を圧縮室に逃がすようにして前記第２の空間内の圧力を調整する第３の油漏出路とを備え、
前記第２の油漏出路は、旋回スクロールの鏡板面に設けられ、前記第２の空間と前記吸込室とを前記旋回スクロールの旋回運動により間欠的に連通する溝であ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 a base plate, and a orbiting scroll having a spiral wrap that is erected in an end plate and meshing with the fixed scroll to make a turning motion. In a scroll compressor configured to form a suction chamber and a compression chamber by orbiting the orbiting scroll,
A first space formed at the center of the back of the orbiting scroll and stored at the bottom of the hermetic container and led to a pressure close to the discharge pressure;
A second space provided on the back side of the orbiting scroll on the outer peripheral side of the first space and serving as a pressure between the discharge pressure and the suction pressure;
A first oil leakage path for leaking a part of the oil in the first space to the second space;
An oil return passage for returning most of the oil in the first space to the bottom in the sealed container;
A second oil leakage path for leaking part of the oil in the second space to the suction chamber;
According to the difference between the pressure in the compression chamber and the pressure in the second space, the pressure in the second space is adjusted so as to release oil in the second space to the compression chamber. An oil leakage path,
The scroll is characterized in that the second oil leakage path is a groove provided on the end plate surface of the orbiting scroll, and intermittently communicating the second space and the suction chamber by the orbiting movement of the orbiting scroll. Compressor. 請求項１〜９の何れか一項に記載のスクロール圧縮機において、断熱指数が１．０９より大きい冷媒を作動流体としていることを特徴とするスクロール圧縮機。 The scroll compressor as described in any one of Claims 1-9 WHEREIN: The refrigerant | coolant whose heat insulation index is larger than 1.09 is made into a working fluid, The scroll compressor characterized by the above-mentioned. 請求項１〜１０の何れか一項に記載のスクロール圧縮機を用いて構成した冷凍空調用の冷凍サイクル装置。 A refrigeration cycle apparatus for refrigeration and air conditioning configured using the scroll compressor according to any one of claims 1 to 10 .
JP2014200554A 2014-09-30 2014-09-30 Scroll compressor and refrigeration cycle apparatus using the same Active JP6302813B2 (en)

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JP2014200554A JP6302813B2 (en) 2014-09-30 2014-09-30 Scroll compressor and refrigeration cycle apparatus using the same
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US15/511,323 US20170306951A1 (en) 2014-09-30 2015-09-29 Scroll compressor and refrigeration cycle apparatus using the same
CN201580052774.1A CN106795881B (en) 2014-09-30 2015-09-29 Screw compressor and the freezing cycle device for having used the screw compressor
PCT/JP2015/077515 WO2016052503A1 (en) 2014-09-30 2015-09-29 Scroll compressor and refrigeration cycle device using same
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CN109026706A (en) 2018-12-18
CN108980036A (en) 2018-12-11
US20170306951A1 (en) 2017-10-26
CN109026706B (en) 2020-06-09
JP2016070178A (en) 2016-05-09
WO2016052503A1 (en) 2016-04-07
CN106795881B (en) 2018-07-31
CN108980036B (en) 2021-02-02

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