JP4512479B2 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
JP4512479B2
JP4512479B2 JP2004345124A JP2004345124A JP4512479B2 JP 4512479 B2 JP4512479 B2 JP 4512479B2 JP 2004345124 A JP2004345124 A JP 2004345124A JP 2004345124 A JP2004345124 A JP 2004345124A JP 4512479 B2 JP4512479 B2 JP 4512479B2
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end plate
scroll
plate surface
fixed scroll
back pressure
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JP2006152930A (en
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雅嗣 近野
健一 大島
康弘 岸
昌浩 島田
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Hitachi Appliances Inc
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Hitachi Appliances Inc
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Priority to JP2004345124A priority Critical patent/JP4512479B2/en
Priority to TW094127329A priority patent/TWI266830B/en
Priority to KR1020050079707A priority patent/KR100739373B1/en
Priority to CNB2005100995947A priority patent/CN100458161C/en
Publication of JP2006152930A publication Critical patent/JP2006152930A/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
    • 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)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (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、台板に渦巻状のラップを立設してなる固定スクロールと鏡板に渦巻状のラップを立設してなる旋回スクロールとを有している。両スクロールの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、スクロール圧縮機は流体を圧縮する。   The scroll compressor has a fixed scroll in which a spiral wrap is erected on a base plate and a revolving scroll in which a spiral wrap is erected on an end plate. The scroll compressor compresses the fluid by engaging the scrolls with the wraps facing each other and rotating the orbiting scroll to sequentially reduce the volumes of the plurality of compression chambers formed between the wraps.

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。両スクロールが引離されてしまうと、ラップの歯先と歯底との間にギャップが生じて圧縮室の密閉性が悪化し、圧縮機の効率が低下する。   Due to this compression action, an axial force (hereinafter referred to as a pulling force) that causes the fixed scroll and the orbiting scroll to separate from each other is generated. When both scrolls are pulled apart, a gap is generated between the tooth tip and the tooth bottom of the wrap, the sealing performance of the compression chamber is deteriorated, and the efficiency of the compressor is lowered.

そこで、旋回スクロールの鏡板の背面に、吐出圧力と吸込圧力の間の圧力となる背圧室を形成し、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、旋回スクロールを固定スクロールに押付ける力を発生させている。   Therefore, a back pressure chamber is formed on the back of the end plate of the orbiting scroll, which is a pressure between the discharge pressure and the suction pressure, and the orbiting scroll is pressed to the fixed scroll side by the back pressure to counteract the pulling force and A force for pressing the scroll against the fixed scroll is generated.

しかし、この押付け力により固定スクロールと旋回スクロールの鏡板面には摺動摩擦が生じ、押付け力が過大となった場合には鏡板面で焼きつき現象が起こり、圧縮機の信頼性が損なわれる。   However, this pressing force causes sliding friction on the end plate surfaces of the fixed scroll and the orbiting scroll, and if the pressing force is excessive, a seizure phenomenon occurs on the end plate surface and the reliability of the compressor is impaired.

鏡板面での摺動損失を低減し、また圧縮機の信頼性を高めるため、特許文献１に記載のスクロール圧縮機では、鏡板面に円弧形状または直線形状等からなる複数の油溝を略等ピッチで配設することにより、摺動部に確実に潤滑油を供給する構造としている。   In order to reduce sliding loss on the end plate surface and increase the reliability of the compressor, in the scroll compressor described in Patent Document 1, a plurality of oil grooves formed in an arc shape or a linear shape are substantially equal on the end plate surface. By arranging them at a pitch, a structure is provided in which lubricating oil is reliably supplied to the sliding portion.

特開平７−２０８３５６号公報JP-A-7-208356

特許文献1に開示の技術は、鏡板面に複数の油溝を略等ピッチで設けるものであり、鏡板面の潤滑状態は良好になる。しかし、鏡板面での、背圧室から吸込室または圧縮室への流体の漏れに対しては特に考慮されていなかった。   The technique disclosed in Patent Document 1 provides a plurality of oil grooves on the end plate surface at a substantially equal pitch, and the end plate is lubricated in a good state. However, no special consideration has been given to fluid leakage from the back pressure chamber to the suction chamber or the compression chamber on the end plate surface.

本発明は、鏡板面での漏れ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 the leak in an end plate surface.

上述の課題を解決するために、本発明のスクロール圧縮機は、
台板に立設された渦巻状のラップと、このラップの先端面と連続して当該ラップの周囲に設けられた鏡板面とを有する固定スクロールと、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とこのラップが立設された鏡板とを有する旋回スクロールと、前記旋回スクロールの鏡板を前記固定スクロールの鏡板面に押し付ける、前記圧縮室で圧縮されたガスの圧力と前記圧縮室に吸込まれるガスの圧力との間の圧力を有する背圧室と、互いに対向して摺動する前記旋回スクロール鏡板の鏡板面と前記固定スクロールの鏡板面との少なくともいずれか一方の鏡板面に前記背圧室の圧力が導入される背圧空間と、を備え、
前記固定スクロールラップの巻き終わり部近傍に設けられた吸込圧領域と、前記固定スクロールラップの渦巻中心に対して対称な前記固定スクロールの鏡板面に前記背圧空間が設けられたことを特徴とする。 In order to solve the above-described problems, a scroll compressor according to the present invention includes:
A fixed scroll having a spiral wrap erected on the base plate, and a mirror plate surface provided continuously around the tip end surface of the wrap, and a plurality of wraps between the fixed scroll wrap A orbiting scroll having a spiral wrap forming a compression chamber and an end plate on which the wrap is erected, and a pressure of gas compressed in the compression chamber pressing the end plate of the orbiting scroll against the end plate surface of the fixed scroll And at least one of the back pressure chamber having a pressure between the pressure of the gas sucked into the compression chamber and the end plate surface of the orbiting scroll end plate that slides facing each other and the end plate surface of the fixed scroll comprising of a back pressure space pressure of the back pressure chamber to the end plate surface is introduced, and
The back pressure space is provided in the suction pressure region provided near the winding end portion of the fixed scroll wrap and the end plate surface of the fixed scroll which is symmetric with respect to the spiral center of the fixed scroll wrap. .

本発明によれば、固定スクロールと旋回スクロールの鏡板面での、背圧室から吸込室または圧縮室への漏れ損失を低減することができる。   According to the present invention, it is possible to reduce leakage loss from the back pressure chamber to the suction chamber or the compression chamber on the end plate surfaces of the fixed scroll and the orbiting scroll.

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１に示すように、固定スクロール７は、円板状の台板７ａと、この台板７ａの上に渦巻き状に立設されたラップ７ｂと、台板７ａの外周側に位置し、ラップ７ｂの先端面と連続する鏡板面を有してラップ７ｂを囲む筒状の支持部７ｄとを有する。   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. As shown in FIG. 1, the fixed scroll 7 is located on the outer peripheral side of the base plate 7a, a disc-like base plate 7a, a wrap 7b erected on the base plate 7a in a spiral shape, A cylindrical support portion 7d having a mirror plate surface continuous with the distal end surface of 7b and surrounding the wrap 7b.

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。また、支持部７ｄの、旋回スクロール８の鏡板８ａと接する面は、固定スクロール７の鏡板面７ｅである。   The surface of the base plate 7a on which the wrap 7b is erected is called a tooth bottom 7c because it is between the wraps 7b. Further, the surface of the support portion 7 d that contacts the end plate 8 a of the orbiting scroll 8 is the end plate surface 7 e of the fixed scroll 7.

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。   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き状のラップ８ｂと、鏡板８ａの背面中央に設けられたボス部８ｄとを有する。また、鏡板８ａの外周部の、固定スクロール７と接する表面が、旋回スクロール８の鏡板面８ｅとなっている。   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. As with the wrap 7b of the disc-shaped end plate 8a and the fixed scroll 7, the orbiting scroll 8 has a spiral wrap 8b erected from the tooth bottom 8c that is the surface of the end plate 8a, and the center of the back of the end plate 8a. And a provided boss portion 8d. 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.

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、密閉構造をなす。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。   The casing 9 houses a scroll portion including the fixed scroll 7 and the orbiting scroll 8, a motor 16, and lubricating oil, and forms a sealed structure. 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.

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は旋回スクロール８のボス部８ｄに設けられた旋回軸受１１に取り付けられ、旋回スクロール８がシャフト１０に回転可能に取り付けられている。このとき、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に周方向に所定角度だけずらして重ね合わせられている。   A crank 10 a is provided at the tip of the shaft 10, the crank 10 a is attached to the orbiting bearing 11 provided on the boss portion 8 d of the orbiting scroll 8, and the orbiting scroll 8 is rotatably attached to the shaft 10. At this time, the orbiting scroll 8 is in a state where the 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.

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。   An Oldham ring 12 is attached as a mechanism for causing the orbiting scroll 8 to relatively rotate with respect to the fixed scroll 7 while restraining it from rotating.

また鏡板面７ｅの外周部分に設けられた環状溝１９は、鏡板面７ｅから所定高さ異なる面を備え、その上を旋回スクロール８の鏡板面８ｅの端部が旋回スクロール８の公転運動に伴い通過する。このような環状溝１９は背圧空間に面しているので、旋回スクロール８の鏡板面８ｅの端部は、旋回スクロール８の公転運動に伴い環状溝１９に重なっても背圧空間に鏡板面８ｅが開放された状態になる。   The annular groove 19 provided in the outer peripheral portion of the end plate surface 7e is provided with a surface having a predetermined height different from the end plate surface 7e, and the end portion of the end plate surface 8e of the orbiting scroll 8 is accompanied by the revolving motion of the orbiting scroll 8. pass. Since such an annular groove 19 faces the back pressure space, even if the end portion of the end plate surface 8e of the orbiting scroll 8 overlaps with the annular groove 19 due to the revolving motion of the orbiting scroll 8, the end plate surface does not enter the back pressure space. 8e is opened.

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、図２に示すように旋回スクロールラップ８ｂ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。また、吸込室２３は、流体を吸入している途中の空間である。この吸込室２３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。   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, as shown in FIG. 2, the turning inner line side compression chamber 13a and the turning outer line side compression chamber 13b are formed on the inner line side and the outer line side of the orbiting scroll wrap 8b, respectively. The suction chamber 23 is a space in the middle of sucking fluid. The suction chamber 23 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.

吸込ポート１４は、固定スクロール７に設けられている。この吸込ポート１４は吸込室２３と連通するように台板７ａの外周側に穿設されている。吸込ポート１４から流入する流体は、吸込室２３により閉じこまれ、新たに吸込室２３と連通するまでは、吸込圧力で存在する。この流体が吸込圧でいる領域が吸込圧領域である。大概はこの吸込圧領域は固定スクロールラップ７ｂの巻き終わり部分近傍に位置する。そのため、この吸込圧領域近傍の固定スクロール鏡板面７ｅは半径方向の長さが短くシール距離が十分取りづらい部分である。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. The suction port 14 is formed on the outer peripheral side of the base plate 7 a so as to communicate with the suction chamber 23. The fluid flowing in from the suction port 14 is confined by the suction chamber 23 and remains at the suction pressure until it newly communicates with the suction chamber 23. The area where this fluid is at the suction pressure is the suction pressure area. Generally, this suction pressure region is located in the vicinity of the winding end portion of the fixed scroll wrap 7b. Therefore, the fixed scroll end plate surface 7e in the vicinity of the suction pressure region is a portion having a short radial length and a seal distance that is difficult to obtain. Further, 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.

次にそ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。   Next, the operation 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 movement.

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、吸込ポート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、ケース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。   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. Thereby, 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 is supplied from the discharge pipe 6 to the refrigeration cycle, for example, through the case 9.

一方、潤滑油はケース９の底に貯留され、周囲の圧力は吐出圧力になっている。フレーム１７、シャフト１０、固定スクロール７、旋回スクロール８で形成された背圧室１８内の圧力は吐出圧より低いため、ケース９の底に貯留している潤滑油はシャフト１０に設けた貫通穴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。   On the other hand, the lubricating oil is stored at the bottom of the case 9, and the surrounding pressure is the discharge pressure. Since the pressure in the back pressure chamber 18 formed by the frame 17, the shaft 10, the fixed scroll 7 and the orbiting scroll 8 is lower than the discharge pressure, the lubricating oil stored in the bottom of the case 9 is a through hole provided in the shaft 10. 3 flows into the back pressure chamber 18. 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.

また、他の潤滑油は、貫通穴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力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２３への連通路に設けられた背圧調整弁２を開いて吸込室２３へ入る。そして、圧縮室１３を通って吐出ポート１５から吐出された潤滑油は、その一部が吐出パイプ６から冷凍サイクルへ吐出され、残りがケース９内で冷媒と分離されて底に貯留する。   Further, the other lubricating oil reaches the upper part of the crank 10 a of the shaft 10 through the through hole 3, lubricates the slewing 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 23 and enters the suction chamber 23. A part of the lubricating oil discharged from the discharge port 15 through the compression chamber 13 is discharged from the discharge pipe 6 to the refrigeration cycle, and the rest is separated from the refrigerant in the case 9 and stored at the bottom.

次に、両スクロールの鏡板面での流体の漏れについて説明する。スクロール圧縮機では、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が発生する。両スクロールが引離されてしまうと、圧縮室の密閉性が悪化して圧縮機の効率が低下する。   Next, fluid leakage on the end plate surface of both scrolls will be described. In the scroll compressor, an axial force for separating the fixed scroll 7 and the orbiting scroll 8 from each other is generated by the compression action. If both scrolls are pulled apart, the sealing performance of the compression chamber deteriorates and the efficiency of the compressor decreases.

そこで、旋回スクロール８の鏡板の背面側を、吐出圧力と吸込圧力の間の圧力となる背圧とする背圧室１８を設け、その背圧により引離し力を打ち消すとともに、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、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は互いに摺動することになる。   Therefore, a back pressure chamber 18 is provided on the back side of the end plate of the orbiting scroll 8 as a back pressure which is a pressure between the discharge pressure and the suction pressure. The scroll 7 is pressed. At this time, the end plate surface 8e of the orbiting scroll 8 and the end plate surface 7e of the fixed scroll 7 slide on each other.

この鏡板での摺動面は、微小なすき間をもって相対しており、図４に示すように、背圧室１８と吸込室２３または圧縮室１３を隔てる役割をしている。この摺動面のすき間の大きさは、鏡板面上の位置および時間により変化する。その理由を以下に述べる。   The sliding surfaces of the end plate are opposed to each other with a minute gap, and serve to separate the back pressure chamber 18 from the suction chamber 23 or the compression chamber 13 as shown in FIG. The size of the clearance between the sliding surfaces varies depending on the position on the end plate surface and time. The reason is described below.

運転時の旋回スクロール８には、圧縮作用により、軸方向の力だけでなく接線方向および半径方向の力も生じており、また遠心力も生じている。これらの力により旋回スクロール８を傾けようとする、いわゆる転覆モーメントが発生する。このため旋回スクロール８は揺動運動をしており、両鏡板面は常に平行とはなっておらず、すき間の大きさも常に一定ではない。このすき間が小さいほど、鏡板面での漏れは小さくなる。   In the orbiting scroll 8 during operation, not only an axial force but also a tangential and radial force are generated by the compression action, and a centrifugal force is also generated. These forces generate a so-called rollover moment that tends to tilt the orbiting scroll 8. For this reason, the orbiting scroll 8 is oscillating, the two end plate surfaces are not always parallel, and the size of the gap is not always constant. The smaller this gap, the smaller the leakage at the end plate surface.

また、鏡板面での漏れは、図２および図５に示したシール長さにも影響を受ける。シール長さとは、固定スクロール７と旋回スクロール８の鏡板摺動面の半径方向の長さであり、背圧室１８と圧縮室１３または吸込室２３とを隔てる長さである。 Also, leakage in the end plate surface also affected the seal length shown in FIGS. 2 and 5. The seal length is the length in the radial direction of the end plate sliding surfaces of the fixed scroll 7 and the orbiting scroll 8 and is the length separating the back pressure chamber 18 from the compression chamber 13 or the suction chamber 23.

例えば、吸込ポート１４付近でのシール長さは、図２（Ａ）では点２４と点２５間の長さ、図２（Ｃ）では点２４と点２６間の長さである。ここで、点２４は固定スクロール内線の最外周上の点であり、点２５は固定スクロール鏡板面７ｅに設けた環状溝１９の内周上の点、点２６は旋回スクロール鏡板外周上の点である。   For example, the seal length near the suction port 14 is the length between the points 24 and 25 in FIG. 2A and the length between the points 24 and 26 in FIG. Here, the point 24 is a point on the outermost periphery of the fixed scroll extension line, the point 25 is a point on the inner periphery of the annular groove 19 provided on the fixed scroll end plate surface 7e, and the point 26 is a point on the outer periphery of the orbiting scroll end plate. is there.

旋回スクロールの旋回運動の位相によってそのシール長さは変化し、各位相におけるシール長さは、点２４と点２５間の長さまたは点２４と点２６間の長さのいずれか短い方の長さとなる。ちなみに環状溝１９がない場合には、点２４と点２６間の長さとなり、１回転中に旋回半径の２倍の長さの分だけ増減することになる。以降のシール長さは、便宜上、１回転中のシール長さの最小値を表すこととする。   The seal length varies depending on the phase of the orbiting movement of the orbiting scroll, and the seal length in each phase is the shorter of the length between the points 24 and 25 or the length between the points 24 and 26, whichever is shorter. It becomes. Incidentally, when there is no annular groove 19, it becomes the length between the point 24 and the point 26, and increases or decreases by the length twice the turning radius during one rotation. The subsequent seal length represents the minimum value of the seal length during one rotation for convenience.

シール長さが短いほど密閉性は悪化し漏れ損失が増大する。シール長さは鏡板面上の位置によって異なり、従来のスクロール圧縮機では、吸込ポート１４付近でのシール長さが最も短いため、吸込ポート１４付近の鏡板面での漏れ損失が、鏡板面上の他の部分に比べて大きいことになる。   The shorter the seal length, the worse the sealing and leakage loss increases. The seal length varies depending on the position on the end plate surface, and in the conventional scroll compressor, the seal length near the suction port 14 is the shortest, so that leakage loss on the end plate surface near the suction port 14 is reduced on the end plate surface. It will be larger than other parts.

さらに、吸込ポート１４付近では、シール前後の圧力差が、背圧と吸込圧力の差となっており、背圧と圧縮室内圧力の差となる鏡板面上の他の部分に比べてより一層漏れが大きい。本発明は、この漏れの大きい吸込ポート１４付近において、旋回スクロール８を固定スクロール７に押付ける力を大きくして、鏡板面間のすき間を小さくし、漏れを低減するものである。   Further, in the vicinity of the suction port 14, the pressure difference before and after the seal is the difference between the back pressure and the suction pressure, which is further leaked as compared with other portions on the end plate surface that are the difference between the back pressure and the pressure in the compression chamber. Is big. In the present invention, the force for pressing the orbiting scroll 8 against the fixed scroll 7 is increased in the vicinity of the suction port 14 where the leakage is large, thereby reducing the gap between the end plate surfaces and reducing the leakage.

本実施の形態の構成について、更に詳細に説明する。図３に示すように、固定スクロール７の鏡板面７ｅに溝１が設けられている。溝１は、環状溝１９に開口しており背圧室１８とは殆ど絞りとならずに流体が連通する空間となる。この溝１は、シール長さの最も短い吸込ポート１４付近に対して、渦巻中心２０を基準として略点対称となる位置を通るように設けられている。そして周方向としては、点対称で溝１を反対側に写すと、吸込みポート１４付近、例えば少なくとも吸込圧領域をカバーする長さを周方向に備える。   The configuration of the present embodiment will be described in more detail. As shown in FIG. 3, the groove 1 is provided on the end plate surface 7 e of the fixed scroll 7. The groove 1 is open to the annular groove 19, and becomes a space in which fluid communicates with the back pressure chamber 18 without being almost throttled. This groove 1 is provided so as to pass through a position that is substantially point-symmetric with respect to the vicinity of the suction port 14 having the shortest seal length with respect to the spiral center 20. As the circumferential direction, when the groove 1 is point-symmetrically copied to the opposite side, the circumferential direction has a length covering the vicinity of the suction port 14, for example, at least the suction pressure region.

図示された固定スクロール７は、外側から順に、フレーム１７に固定する為のボルト等の締結具が取り付けられる支持部７ｄ、環状溝１９、鏡板面７ｅ及び鏡板面７ｅの内側側壁をその一部として渦巻中心２０に対して渦巻き状に巻き回されたラップ７ｂ、が並んでいる。溝１は、見方を変えると環状溝１９の一部が鏡板面７ｅに対して広がった形状、または中心２０の方向に環状溝の溝幅が広がったものである。また溝1は、固定スクロール７の鏡板面７ｅに設けられた段差である。例えば環状溝１９を有してなくても、鏡板面７ｅに設けられた段差である溝１により背圧が導入される。   The illustrated fixed scroll 7 includes, in order from the outside, a support portion 7d to which a fastener such as a bolt for fixing to the frame 17 is attached, an annular groove 19, an end plate surface 7e, and an inner side wall of the end plate surface 7e. Wraps 7b wound in a spiral shape with respect to the spiral center 20 are arranged. In other words, the groove 1 has a shape in which a part of the annular groove 19 is expanded with respect to the end plate surface 7e, or the groove width of the annular groove is increased in the direction of the center 20. The groove 1 is a step provided on the end plate surface 7 e of the fixed scroll 7. For example, even if the annular groove 19 is not provided, the back pressure is introduced by the groove 1 which is a step provided on the end plate surface 7e.

次に、本実施の形態の特徴構成の作用について説明する。図４は、旋回スクロール８の鏡板面８ｅに生じる圧力分布を模式的に示したものである。図４は溝１を設けた場合、図５は溝１を設けない場合の圧力分布である。   Next, the operation of the characteristic configuration of the present embodiment will be described. FIG. 4 schematically shows the pressure distribution generated on the end plate surface 8 e of the orbiting scroll 8. 4 shows the pressure distribution when the groove 1 is provided, and FIG. 5 shows the pressure distribution when the groove 1 is not provided.

溝１を設けた場合、溝１内の圧力が背圧となるため、溝１を設けない場合に比べて、三角形で表される領域２２の分だけ、旋回スクロール８の鏡板面８ｅを上から押す力が増えることになる。つまり、旋回スクロール８の鏡板面８ｅの、溝１に対応する領域を上から下へ押す方向のモーメントが、転覆モーメントに加えて新たに生じることになる。   When the groove 1 is provided, the pressure in the groove 1 becomes a back pressure. Therefore, compared to the case where the groove 1 is not provided, the end plate surface 8e of the orbiting scroll 8 is moved from the top by the region 22 represented by a triangle. The pushing force will increase. That is, a moment in the direction of pushing the region corresponding to the groove 1 on the end plate surface 8e of the orbiting scroll 8 from the top to the bottom is newly generated in addition to the rollover moment.

このとき、旋回スクロール鏡板面８ｅの、渦巻中心２０を基準として溝１に対応する位置と略点対称となる逆側の領域は、固定スクロール７の鏡板面７ｅに押付けられることになる。その押付けられる部分を、鏡板面のシール長さが最も短い部分になるように溝１の位置を調整することで、シール長さが短い部分での押付力を増大させることができ、漏れ損失を低減できる。   At this time, the region on the opposite side of the orbiting scroll mirror plate surface 8 e that is substantially point-symmetric with the position corresponding to the groove 1 with respect to the spiral center 20 is pressed against the mirror plate surface 7 e of the fixed scroll 7. By adjusting the position of the groove 1 so that the pressed portion of the end plate surface has the shortest seal length, the pressing force at the portion with the short seal length can be increased, and leakage loss can be reduced. Can be reduced.

なお、溝１と環状環状溝１９の接続部分２１は、円弧で形成する等の方法により、できるだけ尖らないよう滑らかに仕上げるのがよい。これは、もし鏡板面に設けた溝の端部に尖った部分があれば、揺動運動により旋回スクロール８が傾いた時に接触する可能性があり、鏡板面を損傷するおそれがあるためである。   The connecting portion 21 between the groove 1 and the annular ring groove 19 is preferably finished so as to be as sharp as possible by a method such as forming an arc. This is because if there is a pointed portion at the end of the groove provided on the end plate surface, there is a possibility of contact when the orbiting scroll 8 is tilted by a swinging motion, which may damage the end plate surface. .

上記実施の形態では、固定スクロール７の鏡板面７ｅに溝１を設ける例について説明したが、溝１は図６に示すような形状でもよい。すなわち、図６に示す溝１は、文字通り背圧空間から引き込まれた溝であり、内部が背圧と等しい圧力空間となる。そこでその溝１の空間に対して、渦巻中心２０を基準に反対側の、吸入ポート１４に連通する吸込圧力空間近傍のラップ７ｂと鏡板面７ｅ、特に背圧空間である環状溝１９に近い鏡板面７ｅに対して、旋回スクロール８の鏡板面８ｅを押し付ける作用をもたらす。   In the above embodiment, the example in which the groove 1 is provided on the end plate surface 7e of the fixed scroll 7 has been described. However, the groove 1 may have a shape as shown in FIG. That is, the groove 1 shown in FIG. 6 is literally a groove drawn from the back pressure space, and the inside becomes a pressure space equal to the back pressure. Therefore, the lap 7b and the end plate surface 7e in the vicinity of the suction pressure space communicating with the suction port 14 on the opposite side of the spiral center 20 with respect to the space of the groove 1, particularly the end plate close to the annular groove 19 which is the back pressure space. An effect of pressing the end plate surface 8e of the orbiting scroll 8 against the surface 7e is brought about.

また、図７およびその断面図である図８に示すように、旋回スクロール８の鏡板面８ｅに溝１を設けても同等の機能を実現できる。この場合、構造的には旋回スクロール８の鏡板面８ｅに対する段差部である。鏡板面７ｅに対して環状溝から延びる溝１も鏡板面７ｅに対してみれば段差部であり、背圧導入空間である。   Further, as shown in FIG. 7 and FIG. 8 which is a cross-sectional view thereof, even if the groove 1 is provided on the end plate surface 8e of the orbiting scroll 8, the same function can be realized. In this case, it is structurally a step portion with respect to the end plate surface 8e of the orbiting scroll 8. The groove 1 extending from the annular groove with respect to the end plate surface 7e is also a step when viewed from the end plate surface 7e, and is a back pressure introduction space.

本発明の一実施例におけるスクロール圧縮機の縦断面図。The longitudinal cross-sectional view of the scroll compressor in one Example of this invention. 図１における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した平面図。The top view which showed the compression chamber comprised by the turning scroll and fixed scroll in FIG. 図１における固定スクロールの平面図。The top view of the fixed scroll in FIG. 鏡板面での圧力分布を模式的に示した図。The figure which showed typically the pressure distribution in an end plate surface. 鏡板面での圧力分布を模式的に示した図。The figure which showed typically the pressure distribution in an end plate surface. 本発明の他の実施例における固定スクロールの平面図。The top view of the fixed scroll in the other Example of this invention. 本発明のさらに他の実施例における旋回スクロールの平面図。The top view of the turning scroll in the further another Example of this invention. 図７のＡ−Ａ断面図。AA sectional drawing of FIG.

符号の説明Explanation of symbols

１ 固定スクロールに設けた溝
７ 固定スクロール
８ 旋回スクロール
1 Groove provided on fixed scroll 7 Fixed scroll 8 Orbiting scroll

Claims (5)

台板に立設された渦巻状のラップと、このラップの先端面と連続して当該ラップの周囲に設けられた鏡板面とを有する固定スクロールと、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とこのラップが立設された鏡板とを有する旋回スクロールと、前記旋回スクロールの鏡板を前記固定スクロールの鏡板面に押し付ける、前記圧縮室で圧縮されたガスの圧力と前記圧縮室に吸込まれるガスの圧力との間の圧力を有する背圧室と、互いに対向して摺動する前記旋回スクロール鏡板の鏡板面と前記固定スクロールの鏡板面との少なくともいずれか一方の鏡板面に前記背圧室の圧力が導入される背圧空間と、を備え、
前記固定スクロールラップの巻き終わり部近傍に設けられた吸込圧領域と、前記固定スクロールラップの渦巻中心に対して対称な前記固定スクロールの鏡板面に前記背圧空間が設けられたスクロール圧縮機。 A fixed scroll having a spiral wrap erected on the base plate, and a mirror plate surface provided continuously around the tip end surface of the wrap, and a plurality of wraps between the fixed scroll wrap A orbiting scroll having a spiral wrap forming a compression chamber and an end plate on which the wrap is erected, and a pressure of gas compressed in the compression chamber pressing the end plate of the orbiting scroll against the end plate surface of the fixed scroll And at least one of the back pressure chamber having a pressure between the pressure of the gas sucked into the compression chamber and the end plate surface of the orbiting scroll end plate that slides facing each other and the end plate surface of the fixed scroll comprising of a back pressure space pressure of the back pressure chamber to the end plate surface is introduced, and
A scroll compressor in which the back pressure space is provided on a suction pressure region provided in the vicinity of a winding end portion of the fixed scroll wrap, and an end plate surface of the fixed scroll that is symmetric with respect to a spiral center of the fixed scroll wrap. 請求項１において、前記背圧空間の周方向の長さは、少なくとも前記吸込圧領域の周方向の長さと等しい長さか若しくはそれ以上であるスクロール圧縮機。 The scroll compressor according to claim 1 , wherein the circumferential length of the back pressure space is at least equal to or longer than the circumferential length of the suction pressure region. 請求項１において、前記背圧空間は、互いに対向して摺動する前記旋回スクロール鏡板の鏡板面と前記固定スクロールの鏡板面の少なくともいずれか一方の対向面に設けられた段差部であるスクロール圧縮機。   2. The scroll compression according to claim 1, wherein the back pressure space is a stepped portion provided on at least one of the end plate surface of the orbiting scroll end plate and the end plate surface of the fixed scroll that slide to face each other. Machine. 請求項１において、前記固定スクロールの鏡板面の外側に環状の溝部を備え、前記背圧空間はその環状の溝部から渦巻中心方向に広がった段差部であるスクロール圧縮機。   2. The scroll compressor according to claim 1, wherein an annular groove portion is provided outside the end plate surface of the fixed scroll, and the back pressure space is a stepped portion extending from the annular groove portion toward the spiral center. 請求項１において、前記固定スクロールラップの巻き終わり近傍に設けられた吸込圧領域の半径方向外側における前記固定スクロールの鏡板面の半径方向長さが、前記背圧空間から前記固定スクロールの圧縮室若しくは吸込室までの前記鏡板面同士が摺動する鏡板摺動距離よりも大きいスクロール圧縮機。   The radial length of the end plate surface of the fixed scroll on the radially outer side of the suction pressure region provided near the end of winding of the fixed scroll wrap according to claim 1, wherein the radial length of the end plate surface of the fixed scroll is from the back pressure space to the compression chamber of the fixed scroll or A scroll compressor having a larger end plate sliding distance than the end plate sliding to the suction chamber.
JP2004345124A 2004-11-30 2004-11-30 Scroll compressor Expired - Fee Related JP4512479B2 (en)

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JP5270993B2 (en) * 2008-07-25 2013-08-21 サンデン株式会社 Scroll type fluid machinery
US8297958B2 (en) 2009-09-11 2012-10-30 Bitzer Scroll, Inc. Optimized discharge port for scroll compressor with tip seals
JP5548586B2 (en) * 2010-10-28 2014-07-16 日立アプライアンス株式会社 Scroll compressor
JP6386750B2 (en) * 2014-03-05 2018-09-05 日立ジョンソンコントロールズ空調株式会社 Scroll compressor
US11976655B2 (en) 2016-05-27 2024-05-07 Copeland Climate Technologies (Suzhou) Co. Ltd. Scroll compressor
JP6765263B2 (en) 2016-09-14 2020-10-07 日立ジョンソンコントロールズ空調株式会社 Scroll compressor
JP2020186710A (en) * 2019-05-17 2020-11-19 日立グローバルライフソリューションズ株式会社 Scroll compressor
CN114026328B (en) * 2019-07-02 2023-11-10 日立江森自控空调有限公司 Scroll compressor and air conditioner using the same
WO2021117490A1 (en) * 2019-12-12 2021-06-17 ダイキン工業株式会社 Scroll compressor

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