WO2011145606A1 - スクロール型流体機械 - Google Patents
スクロール型流体機械 Download PDFInfo
- Publication number
- WO2011145606A1 WO2011145606A1 PCT/JP2011/061297 JP2011061297W WO2011145606A1 WO 2011145606 A1 WO2011145606 A1 WO 2011145606A1 JP 2011061297 W JP2011061297 W JP 2011061297W WO 2011145606 A1 WO2011145606 A1 WO 2011145606A1
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- WIPO (PCT)
- Prior art keywords
- scroll
- fluid machine
- type fluid
- movable scroll
- groove
- Prior art date
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Classifications
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
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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
- 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
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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
- F04C2240/00—Components
- F04C2240/10—Stators
Definitions
- the present invention relates to a scroll type fluid machine suitable for a refrigeration circuit used for air conditioning of a vehicle.
- This type of scroll type fluid machine is a scroll type fluid machine in which a fixed scroll and a movable scroll cooperate to define a compression chamber or an expansion chamber of a working fluid containing lubricating oil, and a port through which the working fluid passes; A port is opened, and a housing having a pedestal portion on which a thrust load acts on the back side of the end plate of the movable scroll is provided by a partition of the compression chamber or the expansion chamber.
- the housing is formed with a main suction hole that allows the suction port (suction port) to communicate with the suction chambers on the outer periphery of both scrolls, and the suction port is separated from the main suction hole.
- a scroll type compressor in which an auxiliary suction hole communicating with the compressor is formed (see, for example, Patent Document 1).
- the present invention provides a scroll type fluid machine that can effectively improve the durability of the scroll unit and reduce the mechanical loss with a simple configuration.
- the scroll type fluid machine of the present invention is a scroll type fluid machine in which a fixed scroll and a movable scroll cooperate to partition a compression chamber or an expansion chamber of a working fluid containing lubricating oil, and a port through which the working fluid passes;
- a port is provided, and a housing having a pedestal portion on which a thrust load acts on the back side of the end plate of the movable scroll by a partition of the compression chamber or the expansion chamber is provided, and the pedestal portion is recessed in a region including the opening portion of the port.
- a groove portion is provided.
- the groove is formed along an inner peripheral surface of the housing.
- the groove portion has an annular shape along the inner peripheral surface of the housing.
- a cross-sectional area in the movable scroll radial direction becomes smaller.
- the groove has a terminal portion on the opposite side of the opening in the radial direction of the movable scroll with respect to the axis of the shaft connected to the movable scroll.
- a thrust plate is provided between the pedestal portion and the end plate, and the thrust plate receives a thrust load of the movable scroll by a sliding contact surface on which the back surface is slidably contacted.
- the area of the slidable contact surface increases as the thrust plate moves away from the opening.
- the thrust plate has a shape that closes the groove as it is separated from the opening.
- the spiral coordinate origin of the movable scroll is positioned on the opposite side of the opening in the radial direction of the movable scroll with respect to the axis of the shaft connected to the movable scroll.
- the scroll type fluid machine of the present invention is a horizontal type in which the orbiting axis of the movable scroll is horizontal.
- the working fluid that has passed through the suction port provided in the housing is compressed in the compression chamber defined by the movable scroll and the fixed scroll.
- the working fluid expanded in the expansion chamber defined by the movable scroll and the fixed scroll passes through the discharge port provided in the housing and flows out to the outside.
- the pedestal portion has a groove portion recessed in the region including the opening portion of the port, the working fluid passing through the opening portion of the port flows through the groove portion and spreads over a wide area on the back side of the end plate of the movable scroll. Go around.
- the lubricating oil contained in the working fluid is condensed by coming into contact with the wall surface of the groove and flows out of the groove and adheres to the pedestal and the back surface.
- the working fluid itself that has flowed out of the groove reaches the pedestal and the back surface. Since it is directly condensed on and attached to the pedestal portion and the back surface by contact, an oil film can be formed over a wide area on the back surface side.
- the refrigerant flowing through the groove is gradually taken into the partitioned compression chamber, so that the flow stagnates as it is separated from the opening, and an oil film is also formed at the separation from the opening.
- This problem can be solved, although it becomes difficult to cause abnormal wear. Therefore, it is possible to effectively improve the durability of the scroll unit and reduce the mechanical loss with a simple configuration in which the groove is formed in the region including the opening of the pedestal.
- the groove portion is formed along the inner peripheral surface of the housing, so that the housing serves as a guide so that the working fluid and the lubricating oil can be more smoothly distributed over a wide area on the back side. Therefore, an oil film can be formed more effectively over a wide area on the back side.
- the groove portion has an annular shape along the inner peripheral surface of the housing, so that the working fluid can be spread over the entire range on the back side, and more effectively the back side. An oil film can be formed over a wide range.
- the cross-sectional area in the movable scroll radial direction becomes smaller, so that the lubricating oil accumulated in the groove portion is positively removed at the separation portion from the opening portion of the groove portion. Since it can overflow, an oil film can be formed more effectively over a wide area on the back side.
- the groove portion has a terminal portion on the opposite side of the opening portion in the radial direction of the movable scroll with respect to the axis of the shaft connected to the movable scroll, so that the working fluid is spread over a wide range on the back side.
- the position where the lubricating oil accumulated in the groove overflows can be adjusted by adjusting the position of the terminal portion, it can be more effectively spread over a wide area on the back side. Oil film formation is possible.
- the thrust plate is provided between the pedestal portion and the end plate, and the thrust plate receives the thrust load of the movable scroll by the sliding contact surface with which the back surface is slidably contacted.
- the lubricating oil contained in the working fluid flows out of the groove and adheres to the sliding contact surface or the back surface, or the working fluid itself that has flowed out of the groove has the sliding contact surface.
- the film is directly condensed and attached to the back surface, so that an oil film can be formed over a wide range of the back surface.
- the thrust plate has an area of the slidable contact surface that increases as it is separated from the opening, so that the pressure of the working fluid that acts on the slidable contact surface at a position away from the opening of the groove portion, That is, the surface pressure can be actively reduced, and the lubricant can be effectively adhered to the sliding contact surface by such a decrease in the surface pressure, so that an oil film can be more effectively formed on the sliding contact surface. is there.
- the thrust plate can be actively guided to the sliding contact surface without flowing the lubricating oil into the groove portion by forming a shape that closes the groove portion as the thrust plate is separated from the opening portion.
- an oil film can be formed on the sliding contact surface.
- the spiral coordinate origin of the movable scroll is positioned on the opposite side of the opening in the radial direction of the movable scroll with respect to the axis of the shaft connected to the movable scroll.
- the thrust load of the orbiting scroll fluctuates in the vicinity of the spiral coordinate origin of the orbiting scroll, so the fluctuating thrust load can be received by the sliding contact surface where the surface pressure is reduced and the oil film is suitably formed. The durability can be further improved and the mechanical loss can be reduced.
- FIG. 2 is a view showing the inside of a front housing of the compressor of FIG. 1 from the II-II direction. It is the figure which showed the state which the turning of the movable scroll of FIG. 2 advanced 180 degrees by the phase.
- FIG. 4 is a view showing the inside of a front housing of the compressor of FIG. 1 from the IV-IV direction. It is sectional drawing which showed the scroll compressor which concerns on 2nd Embodiment of this invention. It is the figure which showed the inside of the front housing of the compressor of FIG. 5 from VI-VI direction. It is the figure which showed the state which the turning of the movable scroll of FIG. 6 advanced 180 degrees by the phase.
- FIG. 6 is a view showing the inside of the front housing of the compressor of FIG. 5 from the VIII-VIII direction.
- FIG. 1 shows a scroll compressor (scroll type fluid machine) 1 according to a first embodiment of the present invention.
- This compressor 1 is incorporated in a refrigeration circuit for air-conditioning a vehicle, and a refrigerant (actuation) that circulates in the refrigeration circuit. Used to compress fluid).
- the compressor 1 includes a rear housing 2 and a front housing (housing) 4, and a scroll unit 6 is sandwiched between the rear housing 2 and the front housing 4.
- the scroll unit 6 includes a fixed scroll 8 fixed to each of the housings 2 and 4, and a movable scroll 10 assembled so as to mesh with the fixed scroll 8.
- the compressor 1 is a horizontal scroll compressor in which the orbiting axis of the movable scroll 10 is horizontal, and the scroll unit 6 continues a series of processes from suction of refrigerant to compression through discharge by the orbiting movement of the movable scroll 10. And run. More specifically, a discharge chamber 12 is formed in the rear housing 2 between its end plate and the fixed scroll 8 of the scroll unit 6, and this discharge chamber 12 is a discharge hole formed in the end plate 8 a of the fixed scroll 8. It can be connected via a reed valve type discharge valve 14 (not shown), while being connected to a refrigerant circulation path of the refrigeration circuit via a discharge port (not shown) formed in the rear housing 2.
- a refrigerant suction port (port) 16 is recessed in the outer peripheral wall 4 a of the front housing 4, and the refrigerant introduced from the refrigerant circulation path via the suction port 16 is sucked into the scroll unit 6.
- a drive shaft (shaft) 18 is disposed in the front housing 4, and the drive shaft 18 has a large diameter end portion 20 and a small diameter shaft portion 22.
- the large diameter end portion 20 is rotatably supported by the front housing 4 via a needle bearing 24, and the small diameter shaft portion 22 is rotatably supported by the front housing 4 via a ball bearing 26.
- a lip seal 28 is disposed between the small diameter shaft portion 22 and the front housing 4, and the lip seal 28 partitions the front housing 4 in an airtight manner.
- the drive pulley 30 is rotatably supported by the front housing 4 via a bearing 32. ing.
- the driving pulley 30 is connected to an output pulley on the engine side of the vehicle via a belt, and is rotated by receiving power from the engine. Therefore, during driving of the engine, if the electromagnetic clutch in the drive pulley 30 is on, the drive shaft 18 rotates with the drive pulley 30.
- a crank pin 34 protrudes from the large-diameter end 20 of the drive shaft 18 toward the movable scroll 10, and the crank pin 34 supports the boss 40 of the movable scroll 10 via an eccentric bush 36 and a needle bearing 38. ing. Therefore, when the drive shaft 18 is rotated, the movable scroll 10 performs a turning motion via the crank pin 34 and the eccentric bush 36. Further, a rotation prevention mechanism 42 (see FIG. 2) is disposed between the front housing 4 and the end plate 10a of the movable scroll 10.
- the fixed scroll 8 has a fixed spiral 50 integrally formed with the end plate 8a
- the movable scroll 10 also has a movable spiral 52 integrally formed with the end plate 10a.
- the inner and outer surfaces of the fixed and movable spiral bodies 50 and 52 are formed of involute curved surfaces except for the central end portion thereof.
- the discharge hole described above is positioned in the vicinity of the central end portion 54 of the fixed spiral body 50, and a certain clearance is secured between the inner surface of the central end portion 54.
- a fixed tip seal 56 is provided at the tip of the fixed spiral body 50, and a movable tip seal 58 is provided at the tip of the movable spiral body 52.
- the fixed spiral body 50 and the end plate 10 a are slidably contacted with each other via a fixed tip seal 56, and the movable spiral body 52 and the end plate 8 a are slidably contacted with each other via a movable tip seal 58.
- the refrigerant introduced from the suction port 16 by the sliding contact between the fixed and movable scrolls 8 and 10 is sucked into the scroll unit 6 and the fixed and movable scrolls 8 and 10 cooperate to fix the fixed and movable spiral bodies.
- a compression chamber (compression chamber or expansion chamber) 60 for refrigerant gas containing mist-like lubricating oil is defined between 50 and 52, and the above-described series of processes are continuously performed.
- the front housing 4 has a pedestal 62 formed in an annular shape inside the outer peripheral wall 4a.
- the pedestal portion 62 has a compression reaction force generated by the formation of the compression chamber 60 in the axial direction of the drive shaft 18 on the back surface 64 side of the end plate 10 a of the movable scroll 10, in other words, in the rotational axis direction of the movable scroll 10.
- the thrust load generated by a suction hole 68 communicating with the suction port 16 is opened on the pedestal surface 66 of the pedestal portion 62 on the side facing the back surface 64, and a groove portion 72 is recessed in a region including the opening 70 of the suction hole 68. ing.
- FIGS. 1-10 the shapes of the groove 72 and the thrust plate 74 of the present embodiment, and the flow of the lubricating oil contained in the refrigerant gas and the refrigerant gas will be described in detail with reference to FIGS.
- the flow of the refrigerant gas and the lubricating oil is indicated by a solid line for the visible flow, and the flow hidden by the thrust plate is indicated by a broken line.
- the groove 72 is formed in an annular shape having substantially the same cross-sectional area in the radial direction of the movable scroll 10 along the inner peripheral surface 4b of the front housing 4.
- An annular thrust plate 74 is disposed between the pedestal portion 62 and the end plate 10a.
- the back surface 64 is slidably contacted with the thrust plate 74 as the movable scroll 10 is turned, and the back surface 64 is slidably contacted.
- the sliding contact surface 76 of the thrust plate 74 functions as a thrust receiving surface on which the thrust load of the movable scroll 10 acts directly.
- the thrust plate 74 has a convex portion 78 that is convex in the radial direction of the movable scroll 10 so as to block a part of the groove portion 72 so as to expose the rotation prevention mechanism 42 to the back surface 64 side.
- the concave portions 80 that are concave on the side of the rotation prevention mechanism 42 with respect to the groove portion 72 are formed in an annular shape having concave and convex portions in plan view.
- the refrigerant gas introduced from the suction port 16 is discharged from the opening 70 through the suction hole 68, flows through the groove 72 without being interrupted, and reaches the lower part of the front housing 4. In this process, the refrigerant gas is appropriately sucked into the scroll unit 6 and the compression chamber 60 is partitioned.
- the mist-like lubricating oil contained in the refrigerant gas condenses by contacting the wall surface of the groove portion 72, together with the refrigerant gas. Liquid lubricant flows down the groove 72.
- the refrigerant gas introduced from the suction port 16 is discharged from the opening portion 70, flows through the groove portion 72, and flows over a wide area of the sliding contact surface 76. Go around.
- the lubricant contained in the refrigerant gas comes into contact with the wall surface of the groove portion 72 to cause condensation to flow out of the groove portion 72 and adhere to the sliding contact surface 76 or the back surface 64, or the refrigerant gas itself that has flowed out of the groove portion 72.
- the film directly forms dew and adheres to the slidable contact surface 76 and the back surface 64, so that an oil film can be formed over a wide range of the slidable contact surface 76.
- the refrigerant gas flowing through the groove 72 is gradually taken into the partitioned compression chamber 60, so that the flow stagnates as it is separated from the opening 70, and particularly at the lower part in the front housing, the sliding surface 76 Although it is difficult to form an oil film and abnormal wear tends to occur, this problem can be solved. Therefore, the durability of the scroll unit 6 and the reduction of the mechanical loss can be effectively realized with a simple configuration in which the groove 72 is formed in the region including the opening 70 of the pedestal 62.
- the groove portion 72 is formed along the inner peripheral surface 4 b of the front housing 4, so that the front housing 4 serves as a guide so that the refrigerant and therefore the lubricating oil can be more smoothly distributed over a wide range of the sliding contact surface 76. Furthermore, since the groove 72 has an annular shape along the inner peripheral surface 4b of the front housing 4, the refrigerant can be spread over the entire range of the sliding contact surface 76. An oil film can be effectively formed on the slidable contact surface 76 in the lower part of the slab.
- FIG. 5 shows a scroll compressor (scroll type fluid machine) 88 according to the second embodiment of the present invention.
- the same reference numerals are given and the description is omitted, or the reference numerals are omitted.
- the shapes of the groove 90 and the thrust plate 92 according to the present embodiment, and the flow of the lubricating oil contained in the refrigerant gas and the refrigerant gas will be described with reference to FIGS.
- the flow of the refrigerant gas and the lubricating oil is indicated by a solid line for the visible flow
- the flow hidden by the thrust plate is indicated by a broken line.
- the groove 90 is formed in an annular shape along the inner peripheral surface 4 b of the front housing 4 so that the radial sectional area of the movable scroll 10 decreases as the distance from the opening 70 increases.
- the thrust plate 92 is formed to have an enlarged sliding contact portion 96 whose area of the sliding contact surface 94 becomes larger as it is separated from the opening 70, and the enlarged sliding contact portion 96 is a groove portion at the lower part in the front housing 4. 90 is blocked.
- the spiral coordinate origin O of the movable scroll 10 is on the opposite side of the opening 70 in the radial direction of the movable scroll 10 with respect to the axis C of the drive shaft 18 connected to the movable scroll 10. That is, it is positioned on the enlarged sliding contact portion 90 side.
- the groove 90 is separated from the opening 70 as shown in FIG. 8 by reducing the cross-sectional area of the groove 90 as it is separated from the opening 70. Since the lubricating oil collected in the groove 90 can be actively overflowed and guided to the sliding contact surface 94 at the location, that is, the lower portion in the front housing 4, the sliding contact surface 94 at the lower portion in the front housing 4 is further effective. Thus, an oil film can be formed.
- the pressure of the refrigerant acting on the slidable contact surface 94 at the lower part in the front housing 4, that is, the surface pressure of the slidable contact surface 94 can be actively reduced. Due to such a decrease in the surface pressure, the lubricating oil can be effectively attached to the sliding contact surface 94 of the enlarged sliding contact portion 96, so that an oil film is more effectively formed on the sliding contact surface 94 in the lower part of the front housing 4. can do.
- the lubricant can be actively guided to the slidable contact surface 94 of the enlarged slidable contact portion 96 without flowing into the groove portion 90.
- An oil film can be more effectively formed on the sliding contact surface in the lower part.
- the thrust load of the movable scroll 10 generally fluctuates in the vicinity of the spiral coordinate origin O of the movable scroll 10, so that the varying thrust load is Since it can be received by the sliding contact surface 94 of the enlarged sliding contact portion 96 in which the oil pressure is suitably formed by reducing the surface pressure, the durability of the scroll unit 6 can be further improved and the mechanical loss can be reduced.
- the groove portions 72 and 90 of the present invention are not necessarily formed in an annular shape, and a terminal portion (not shown) on the opposite side of the opening portion 70 in the radial direction of the movable scroll 10 with respect to the axis C of the drive shaft 18.
- the grooves 72 and 90 may be formed in an ⁇ shape.
- the refrigerant can be spread over a wide range of the sliding contact surfaces 76 and 94, and the position where the terminal portion is adjusted to overflow the lubricating oil accumulated in the grooves 72 and 90. Therefore, it is possible to more effectively form an oil film on the sliding contact surfaces 76 and 94 at the lower part in the front housing 4.
- the shape of the thrust plates 74 and 92 of the present invention is not limited to the illustrated shape as long as the convex portion 78, the concave portion 80, or the enlarged sliding contact portion 96 is appropriately formed. Further, in the compressor of the present invention, the thrust plates 74 and 92 are not necessarily required, and as long as at least the groove portions 72 and 90 are provided, the structure in which the pedestal surface 66 of the pedestal portion 62 is in sliding contact with the back surface 64 is the same. An effect can be obtained.
- the present invention can be applied not only to a horizontal type scroll compressor but also to a vertical type, and can be applied to all scroll type fluid machines such as a scroll expander in which an expansion chamber for refrigerant is formed.
- scroll type fluid machines such as a scroll expander in which an expansion chamber for refrigerant is formed.
Abstract
Description
そして上記スクロール型流体機械の一例として、ハウジングに、吸入口(吸入ポート)を両スクロールの外周の吸入室に連通させる主吸入孔を形成するとともに、その主吸入孔とは別に吸入口を吸入室に連通する補助吸入孔を形成したスクロール型圧縮機が開示されている(例えば特許文献1参照)。
しかしながら、上記従来技術では、可動スクロールの背面の一部に局所的に異常摩耗が生じるおそれがある点につき格別な配慮がなされておらず、スクロールユニットの更なる潤滑性向上、ひいては効果的な耐久性向上及び機械損失低減を実現することについて依然として課題が残されている。
好ましくは、前記溝部は前記ハウジングの内周面に沿う円環形状をなす。
好ましくは、前記溝部は前記開口部から離間するにつれて前記可動スクロール径方向における断面積が小となる。
好ましくは、前記溝部は前記可動スクロールと連結される軸の軸心を基準に前記可動スクロールの径方向において前記開口部の反対側に終端部を有する(請求項5)。
好ましくは、前記スラストプレートは前記開口部から離間するにつれて前記摺接面の面積が大となる。
好ましくは、前記可動スクロールの渦巻座標原点は前記可動スクロールと連結される軸の軸心を基準に前記可動スクロールの径方向において前記開口部の反対側に位置づけられる。
また、本発明によれば、溝部はハウジングの内周面に沿う円環形状をなすことにより、作動流体を背面側の全範囲に亘って行き渡らせることが可能であり、更に効果的に背面側の広範囲に亘って油膜形成が可能である。
また、本発明によれば、可動スクロールの渦巻座標原点は可動スクロールと連結される軸の軸心を基準に可動スクロールの径方向において開口部の反対側に位置づけられる。一般に可動スクロールのスラスト荷重は可動スクロールの渦巻座標原点近傍で変動することから、変動するスラスト荷重を面圧低下されて油膜が好適に形成されたた摺接面で受けることができるため、スクロールユニットの更なる耐久性向上及び機械損失低減を図ることができる。
圧縮機1はリアハウジング2及びフロントハウジング(ハウジング)4を備え、リアハウジング2とフロントハウジング4との間にはスクロールユニット6が挟持されている。スクロールユニット6は各ハウジング2,4に固定された固定スクロール8と、この固定スクロール8に対して噛み合うように組付けられた可動スクロール10とからなる。
より詳しくは、リアハウジング2内にはその端板とスクロールユニット6の固定スクロール8との間に吐出室12が形成され、この吐出室12は固定スクロール8の端板8aに形成された吐出孔(図示しない)にリードバルブタイプの吐出弁14を介して接続可能である一方、リアハウジング2に形成した吐出ポート(図示しない)を介して冷凍回路の冷媒循環経路に接続されている。
一方、フロントハウジング4内には駆動軸(軸)18が配置され、この駆動軸18は大径端部20及び小径軸部22を有する。大径端部20はニードル軸受24を介してフロントハウジング4に回転自在に支持され、小径軸部22はボール軸受26を介してフロントハウジング4に回転自在に支持されている。更に、小径軸部22とフロントハウジング4との間にはリップシール28が配置され、このリップシール28はフロントハウジング4内を気密に区画している。
更に、フロントハウジング4と可動スクロール10の端板10aとの間には自転阻止機構42(図2参照)が配置されている。
なお、上述した吐出孔は、固定渦巻体50の中央端部54の近傍に位置付けられ、この中央端部54の内面との間には一定のクリアランスが確保されている。
また、冷媒ガスが溝部72を流下する過程において、冷媒ガスの一部はスラストプレート74を超えて溝部72から流出する。この流出した冷媒ガス自体が摺接面76及び背面64に接触することによってミスト状の潤滑油が摺接面76及び背面64に直接に結露して付着されるため、摺接面76に油膜が好適に形成される。
以下、図6~8を参照して、本実施形態の溝部90及びスラストプレート92の形状、及び、冷媒ガス及び冷媒ガスに含まれる潤滑油の流れについて説明する。なお、これらの図中において冷媒ガス及び潤滑油の流れは、見える流れについては実線で示し、スラストプレートで隠れる流れは破線で示す。
上述したように、第2実施形態の圧縮機88では、溝部90の断面積を開口部70から離間するにつれて小さくすることにより、図8に示されるように、溝部90の開口部70からの離間箇所、すなわちフロントハウジング4内の下部においては溝部90に溜まった潤滑油を積極的に溢れさせ、摺接面94に導くことができるため、フロントハウジング4内の下部における摺接面94に更に効果的に油膜を形成することができる。
例えば、本発明の溝部72,90は必ずしも環形状に形成される必要はなく、駆動軸18の軸心Cを基準に可動スクロール10の径方向において開口部70の反対側に終端部(図示しない)を形成し、溝部72,90をΩ状に形成しても良い。この場合にも冷媒を摺接面76,94の広範囲に亘って行き渡らせることが可能であり、しかも、この終端部の位置を調整することによって溝部72,90に溜まった潤滑油を溢れさせる位置をも調整可能となることから、更に効果的にフロントハウジング4内の下部における摺接面76,94に油膜形成が可能である。
更に、本発明の圧縮機では必ずしもスラストプレート74,92を要していなくても良く、少なくとも溝部72,90を有する限りは台座部62の台座面66が背面64に摺接する構造としても同様の効果を得ることが可能である。
4 ハウジング
4b 内周面
8 固定スクロール
10 可動スクロール
10a 端板
16 吸入ポート(ポート)
18 駆動軸(軸)
60 圧縮室(圧縮室または膨張室)
62 台座部
64 背面
72,90 溝部
74,92 スラストプレート
76,94 摺接面
Claims (10)
- 固定スクロール及び可動スクロールが協働して潤滑油を含む作動流体の圧縮室または膨張室を区画するスクロール型流体機械であって、
前記作動流体が通過するポートと、前記ポートが開口され、前記圧縮室または前記膨張室の区画によって前記可動スクロールの端板の背面側にスラスト荷重が作用する台座部とを有するハウジングを備え、
前記台座部は前記ポートの開口部を含む領域に凹設された溝部を有することを特徴とするスクロール型流体機械。 - 前記溝部は前記ハウジングの内周面に沿って形成されることを特徴とする請求項1に記載のスクロール型流体機械。
- 前記溝部は前記ハウジングの内周面に沿う円環形状をなすことを特徴とする請求項1に記載のスクロール型流体機械。
- 前記溝部は前記開口部から離間するにつれて前記可動スクロールの径方向における断面積が小となることを特徴とする請求項1に記載のスクロール型流体機械。
- 前記溝部は前記可動スクロールと連結される軸の軸心を基準に前記可動スクロールの径方向において前記開口部の反対側に終端部を有することを特徴とする請求項1に記載のスクロール型流体機械。
- 前記台座部と前記端板との間にはスラストプレートが設けられ、前記スラストプレートは前記背面が摺接される摺接面によって前記可動スクロールのスラスト荷重を受けることを特徴とする請求項1に記載のスクロール型流体機械。
- 前記スラストプレートは前記開口部から離間するにつれて前記摺接面の面積が大となることを特徴とする請求項6に記載のスクロール型流体機械。
- 前記スラストプレートは前記開口部から離間するにつれて前記溝部を塞ぐ形状をなすことを特徴とする請求項6に記載のスクロール型流体機械。
- 前記可動スクロールの渦巻座標原点は前記可動スクロールと連結される軸の軸心を基準に前記可動スクロールの径方向において前記開口部の反対側に位置づけられることを特徴とする請求項7に記載のスクロール型流体機械。
- 前記可動スクロールの旋回軸線が水平となる横置き型であることを特徴とする請求項1に記載のスクロール型流体機械。
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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US13/698,902 US20130058821A1 (en) | 2010-05-18 | 2011-05-17 | Scroll-Type Fluid Machine |
CN2011800246824A CN102893031A (zh) | 2010-05-18 | 2011-05-17 | 涡旋型流体机械 |
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Application Number | Priority Date | Filing Date | Title |
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JP2010-114158 | 2010-05-18 | ||
JP2010114158A JP5341819B2 (ja) | 2010-05-18 | 2010-05-18 | スクロール型流体機械 |
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WO2011145606A1 true WO2011145606A1 (ja) | 2011-11-24 |
Family
ID=44991708
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PCT/JP2011/061297 WO2011145606A1 (ja) | 2010-05-18 | 2011-05-17 | スクロール型流体機械 |
Country Status (4)
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US (1) | US20130058821A1 (ja) |
JP (1) | JP5341819B2 (ja) |
CN (1) | CN102893031A (ja) |
WO (1) | WO2011145606A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN110886623A (zh) * | 2018-09-07 | 2020-03-17 | 涡旋技研有限公司 | 涡旋式膨胀机 |
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JP3207825B2 (ja) * | 1999-06-23 | 2001-09-10 | 三菱重工業株式会社 | スクロール型流体機械 |
JP2005307949A (ja) * | 2004-04-26 | 2005-11-04 | Sanden Corp | スクロール型流体機械 |
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JPH06264876A (ja) * | 1993-03-15 | 1994-09-20 | Toshiba Corp | スクロ−ル形圧縮機 |
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JP3227075B2 (ja) * | 1994-12-08 | 2001-11-12 | 株式会社デンソー | スクロール型圧縮機 |
US6074186A (en) * | 1997-10-27 | 2000-06-13 | Carrier Corporation | Lubrication systems for scroll compressors |
JP2001055988A (ja) * | 1999-06-08 | 2001-02-27 | Mitsubishi Heavy Ind Ltd | スクロール圧縮機 |
CN1510302A (zh) * | 2002-12-25 | 2004-07-07 | 乐金电子(天津)电器有限公司 | 螺杆式压缩机 |
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KR100877017B1 (ko) * | 2006-06-14 | 2009-01-09 | 미츠비시 쥬고교 가부시키가이샤 | 유체 기계 |
-
2010
- 2010-05-18 JP JP2010114158A patent/JP5341819B2/ja active Active
-
2011
- 2011-05-17 CN CN2011800246824A patent/CN102893031A/zh active Pending
- 2011-05-17 WO PCT/JP2011/061297 patent/WO2011145606A1/ja active Application Filing
- 2011-05-17 US US13/698,902 patent/US20130058821A1/en not_active Abandoned
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JPH08159060A (ja) * | 1994-11-30 | 1996-06-18 | Matsushita Electric Ind Co Ltd | 横置き型スクロール流体機械 |
JP3207825B2 (ja) * | 1999-06-23 | 2001-09-10 | 三菱重工業株式会社 | スクロール型流体機械 |
JP2005307949A (ja) * | 2004-04-26 | 2005-11-04 | Sanden Corp | スクロール型流体機械 |
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CN110886623A (zh) * | 2018-09-07 | 2020-03-17 | 涡旋技研有限公司 | 涡旋式膨胀机 |
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CN102893031A (zh) | 2013-01-23 |
JP2011241748A (ja) | 2011-12-01 |
JP5341819B2 (ja) | 2013-11-13 |
US20130058821A1 (en) | 2013-03-07 |
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