WO2016189738A1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
WO2016189738A1
WO2016189738A1 PCT/JP2015/065437 JP2015065437W WO2016189738A1 WO 2016189738 A1 WO2016189738 A1 WO 2016189738A1 JP 2015065437 W JP2015065437 W JP 2015065437W WO 2016189738 A1 WO2016189738 A1 WO 2016189738A1
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WO
WIPO (PCT)
Prior art keywords
oil
scroll
oldham ring
frame
shell
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Application number
PCT/JP2015/065437
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French (fr)
Japanese (ja)
Inventor
祐司 ▲高▼村
英人 中尾
Original Assignee
三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2015/065437 priority Critical patent/WO2016189738A1/en
Priority to JP2017520190A priority patent/JP6381795B2/en
Publication of WO2016189738A1 publication Critical patent/WO2016189738A1/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

Definitions

  • the present invention relates to a scroll compressor that compresses working gas.
  • a conventional scroll compressor used for a refrigerator or an air conditioner is known in which wear and adhesion of a thrust bearing are suppressed (see, for example, Patent Document 1).
  • the scroll compressor described in Patent Document 1 includes a fixed scroll and a swing scroll, and the swing scroll performs a revolving orbiting motion (swing motion) with respect to the fixed scroll.
  • the fixed scroll and the swing scroll are members in which spiral wrap portions are formed on surfaces facing each other, and a compression chamber is formed by both wrap portions.
  • the lower surface of the base plate of the orbiting scroll is a thrust surface that supports a thrust load, and a thrust bearing is provided below the thrust surface. Then, as the swing scroll swings, the internal volume of the compression chamber changes, and the working gas flowing into the compression chamber is compressed.
  • Patent Document 1 an Oldham ring that converts the rotational motion of the shaft into the swing motion of the orbiting scroll is arranged on the upper surface side of the base plate of the orbiting scroll, and the surface pressure is increased by increasing the area of the thrust bearing. By lowering, the wear and adhesion of the thrust bearing are suppressed.
  • the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a scroll compressor that suppresses an increase in oil rising while suppressing wear and adhesion of a thrust bearing.
  • a scroll compressor comprises an outer shell, an oil reservoir formed in a lower portion, an oil pump housed in the shell and sucking up oil from the oil reservoir, and fixed to the inside of the shell.
  • a fixed scroll a swing scroll that forms a compression chamber that compresses the working gas together with the fixed scroll, a frame fixed to the shell and supporting the compression unit, and supported by the frame.
  • An Oldham ring to be converted, and the frame is formed with an Oldham ring space for accommodating the Oldham ring, and inside the Oldham ring space, Thrust bearing is provided for supporting the thrust load of KiYurado scroll, on the outside of the Oldham ring space, in which the sealing portion for preventing leakage of oil is provided.
  • the amount of deformation of the base plate of the orbiting scroll due to the thrust load can be suppressed by disposing the thrust bearing inside the Oldham ring space. And since an oil film is formed between the thrust surface of the orbiting scroll and the thrust bearing of the frame with a small taper gap, good sliding characteristics can be obtained even with a small thrust area. Wear and adhesion due to sliding in the thrust bearing can be suppressed. Further, by providing the seal portion outside the Oldham ring space, the oil that lubricated the Oldham ring is confined inside the seal portion, so that the oil is sucked into the compression chamber, and an increase in oil rising can be suppressed.
  • FIG. 1 is a schematic axial sectional view of a scroll compressor 1 according to Embodiment 1 of the present invention.
  • the scroll compressor 1 sucks and compresses the refrigerant circulating in the refrigeration cycle, and discharges it in a high-temperature and high-pressure state.
  • the scroll compressor 1 includes a shell 2, an oil pump 3, a motor 4, a compression part 5, a frame 6, and a shaft part 7. Further, the scroll compressor 1 includes a suction pipe 11, a discharge pipe 12, a discharge chamber 13, a muffler 14, an Oldham ring 15, a slider 16, a sleeve 17, a first balancer 18, and a second balancer.
  • the balancer 19, the subframe 20, and the oil drain pipe 21 are provided.
  • the shell 2 constitutes the outer shell of the scroll compressor 1 and has an oil sump 3a formed in the lower part.
  • the shell 2 has, for example, a bottomed cylindrical shape, and the upper portion is closed by a dome-shaped upper shell 2a.
  • the shell 2 is placed on the lower shell 2b.
  • the oil pump 3 is accommodated in the shell 2 and sucks up oil from the oil sump 3a.
  • the oil pump 3 is provided at the lower part of the shell 2.
  • the oil pump 3 lubricates the bearing part inside the scroll compressor 1 with the oil sucked up from the oil reservoir 3a.
  • the oil after lubricating the oscillating bearing is stored in an internal space 6d (see FIG. 4 described later) of the frame 6, and then passes through the radial oil supply groove 6c provided in the thrust bearing 6b, and the Oldham ring space 15b.
  • the Oldham ring space 15 b is provided with a drain oil pipe 21, and the oil is returned to the oil sump 3 a through the drain oil pipe 21.
  • the motor 4 is provided inside the shell 2 and is installed, for example, between the frame 6 and the sub-frame 20 and rotates the shaft portion 7.
  • the motor 4 has a rotor 4a and a stator 4b.
  • the rotor 4 a is provided on the inner peripheral side of the stator 4 b and is attached to the shaft portion 7. And the rotor 4a rotates the axial part 7 by rotating itself.
  • the stator 4b rotates the rotor 4a with electric power supplied from an inverter (not shown).
  • the compression unit 5 is provided inside the shell 2 and is driven by the motor 4 to compress the working gas.
  • the compression unit 5 includes a fixed scroll 30 and a swing scroll 40.
  • the fixed scroll 30 is fixed inside the shell 2 and causes the compressed working gas to flow out into the discharge chamber 13.
  • the orbiting scroll 40 performs a revolving orbiting motion (oscillating motion) with respect to the fixed scroll 30, and the rotation motion is regulated by the Oldham ring 15.
  • the fixed scroll 30 and the swing scroll 40 are members in which spiral wrap portions 31 and a wrap portion 41 are formed on surfaces facing each other.
  • the wrap portion 31 of the fixed scroll 30 and the wrap portion of the swing scroll 40 are provided.
  • a compression chamber 5a is formed in a space where the portion 41 is engaged.
  • the swing scroll 40 is swung by the shaft portion 7, and the working gas is compressed in the formed compression chamber 5a.
  • the frame 6 is fixed to the shell 2 and accommodates the compression portion 5, and for example, rotatably supports the shaft portion 7 via a main bearing 8a.
  • a suction port 6a is formed in the frame 6, and the working gas flows into the compression unit 5 through the suction port 6a.
  • the shaft portion 7 is supported by the frame 6 and has an oil passage 7a through which oil sucked up by the oil pump 3 flows.
  • the shaft portion 7 connects the motor 4 and the compression portion 5 to increase the rotational force of the motor 4. This is transmitted to the compression unit 5.
  • the suction pipe 11 is provided on the side of the shell 2 and sucks the working gas into the shell 2.
  • the discharge pipe 12 is provided on the upper part of the shell 2 and discharges the working gas to the outside of the shell 2.
  • the discharge chamber 13 is provided in the upper part of the compression part 5, and accommodates the working gas which flowed in from the compression part 5.
  • the muffler 14 is provided above the discharge chamber 13 and suppresses pulsation of the working gas discharged from the discharge chamber 13.
  • FIG. 2 is a top view showing the Oldham ring 15 of the scroll compressor 1 according to the first embodiment of the present invention
  • FIG. 3 is a swing scroll 40 of the scroll compressor 1 according to the first embodiment of the present invention.
  • the Oldham ring 15 is an annular member attached to the orbiting scroll 40 as shown in FIG. 2, and restricts the rotational movement of the orbiting scroll 40.
  • the Oldham ring 15 has an Oldham claw 15c and is fitted into an Oldham groove 15a formed on the lower surface of the base plate 43 of the swing scroll 40 shown in FIG.
  • the slider 16 is a cylindrical member attached to the outer peripheral surface of the upper portion of the shaft portion 7, and is located on the inner surface of the lower portion of the swing scroll 40. That is, the orbiting scroll 40 is attached to the shaft portion 7 via the slider 16, and the orbiting scroll 40 rotates as the shaft portion 7 rotates.
  • a rocking bearing 8 c is provided between the rocking scroll 40 and the slider 16.
  • the sleeve 17 is a cylindrical member provided between the frame 6 and the main bearing 8 a and absorbs the inclination between the frame 6 and the shaft portion 7.
  • the first balancer 18 is attached to the shaft 7 and is located between the frame 6 and the rotor 4a.
  • the first balancer 18 cancels the imbalance caused by the orbiting scroll 40 and the slider 16.
  • the first balancer 18 is accommodated in the balancer cover 18a.
  • the second balancer 19 is attached to the shaft portion 7, is located between the rotor 4 a and the sub frame 20, and is attached to the lower surface of the rotor 4 a.
  • the second balancer 19 cancels the imbalance caused by the orbiting scroll 40 and the slider 16.
  • the sub-frame 20 is provided below the motor 4 inside the shell 2 and rotatably supports the shaft portion 7 via the sub-bearing 8b.
  • the oil drain pipe 21 is a pipe that connects the space between the frame 6 and the swing scroll 40 and the space between the frame 6 and the subframe 20.
  • the oil drain pipe 21 causes excess oil out of the oil flowing in the space between the frame 6 and the swing scroll 40 to flow into the space between the frame 6 and the sub-frame 20.
  • the oil that has flowed into the space between the frame 6 and the subframe 20 passes through the subframe 20 and returns to the oil sump 3a.
  • the compression unit 5 includes the fixed scroll 30 and the swing scroll 40 as described above.
  • the fixed scroll 30 is fixed inside the shell 2, and the outer peripheral edge portion is placed on the upper portion of the frame 6.
  • the rocking scroll 40 is provided with a thrust surface 40a for supporting a thrust load on the lower surface, and a thrust bearing 6b for supporting the thrust load is provided on the inner peripheral side of the surface of the frame 6 facing the thrust surface 40a. It has been.
  • the thrust bearing 6b is heat-treated or provided with an oil supply groove 6c, for example, to ensure good slidability. Another member having good slidability may be disposed as the thrust bearing 6b.
  • An Oldham ring space 15b is provided on the outer periphery of the thrust bearing 6b, and the Oldham ring 15 is accommodated in the Oldham ring space 15b.
  • a seal portion 6e is provided on the outer periphery of the Oldham ring space 15b, and a seal surface 6f is formed on the upper surface thereof.
  • the seal portion 6e and the base plate 43 of the orbiting scroll 40 facing the seal surface 6f suppress oil from flowing out from the Oldham ring space 15b to the outer periphery and being sucked into the compression chamber 5a (a later-described figure). 4).
  • FIG. 4 is a top view showing frame 6 of scroll compressor 1 according to Embodiment 1 of the present invention
  • FIG. 5 is a side showing frame 6 of scroll compressor 1 according to Embodiment 1 of the present invention. It is a cross-sectional schematic diagram.
  • a thrust bearing 6b is provided in the frame 6, and a seal portion 6e for preventing oil from leaking to the outer periphery is provided on the outer peripheral side, and between the thrust bearing 6b and the seal portion 6e.
  • the Oldham ring space 15b is formed.
  • the Oldham ring 15 that reciprocates in the Oldham ring space 15b is accommodated in the Oldham ring space 15b.
  • the thrust bearing 6b is provided with oil supply grooves 6c radially, and the oil stored in the internal space 6d inside the thrust bearing 6b passes through the oil supply groove 6c, whereby the thrust bearing 6b and the Oldham ring 15 are lubricated. I do.
  • An oil drain hole 15e communicating with the Oldham ring space 15b is formed in the frame 6, and oil accumulated in the Oldham ring space 15b is discharged from the oil drain pipe 21 through the oil drain hole 15e.
  • the upper surface of the thrust bearing 6b and the seal surface 6f of the seal portion 6e are on the same plane.
  • the base plate of the orbiting scroll 40 is set to have a dimensional relationship of R os ⁇ (R r + R seal )> 0.
  • the lower surface of 43 and the seal surface 6f of the seal portion 6e of the frame 6 overlap without depending on the crank angle of the orbiting scroll 40, and the oil sealability can be ensured.
  • FIG. 6 is a schematic axial sectional view showing the orbiting scroll 40 of the scroll compressor 1 according to Embodiment 1 of the present invention.
  • FIG. 7 is a schematic axial sectional view showing a swing scroll 140 of a conventional scroll compressor.
  • the support span D of the thrust load is shorter than that of the conventional scroll compressor shown in FIG.
  • D 2R thi .
  • the thrust bearing 6b is arranged inside the Oldham ring space 15b, so that the support span D of the thrust load is shorter than the conventional one. Therefore, the base plate 43 of the orbiting scroll 40 is deformed by the thrust load. Can be suppressed. Since a large oil film pressure is generated by the wedge effect and the throttle film effect between the thrust surface 40a of the orbiting scroll 40 and the thrust bearing 6b having a small tapered gap, an oil film is formed. Even with a small thrust area, good sliding characteristics can be obtained, and wear and adhesion due to sliding on the thrust bearing 6b can be suppressed. As a result, the reliability of the thrust bearing 6b can be improved.
  • the seal portion 6e outside the Oldham ring space 15b, the oil that lubricated the Oldham ring 15 is confined inside the seal portion 6e, so that the oil is sucked into the compression chamber 5a and the increase in oil rise is suppressed. can do.
  • the amount of bending of the base plate 143 can be suppressed by increasing the thickness of the base plate 143 of the swing scroll 140, but in this case, the weight of the swing scroll 140 increases.
  • the problem of increased load on the main bearing, sub-bearing, and scroll wrap surface occurs.
  • the oil film pressure is mainly generated on the inner peripheral side of the thrust bearing 6b. Even if the area on the outer peripheral side of the thrust bearing 6b is reduced, the reliability of the thrust bearing 6b is increased. The impact on is small.
  • FIG. 8 is a schematic side sectional view showing the frame 6 of the scroll compressor 1 according to Embodiment 2 of the present invention.
  • the upper portion of the thrust bearing 6b is formed of a member 6g separate from the portion other than the upper portion (and the frame 6).
  • the separate member 6g is, for example, a ring-type bearing metal made of a highly slidable alloy or resin, and the upper portion of the thrust bearing 6b is different from the portions other than the upper portion (and the frame 6).
  • the upper surface of the thrust bearing 6b must surely be higher than the seal surface 6f of the seal portion 6e, and the height h1 from the seal surface 6f of the seal portion 6e to the upper surface of the thrust bearing 6b should be set to 0 to 50 ⁇ m. Thus, good sealing properties can be obtained.
  • FIG. 9 is a schematic axial sectional view showing the orbiting scroll 40 of the scroll compressor 1 according to Embodiment 3 of the present invention.
  • the seal portion 6e is higher than the thrust bearing 6b of the frame 6. That is, the seal surface 6f of the seal portion 6e is arranged on the upper side of the upper surface of the thrust bearing 6b.
  • the thickness of the portion of the base plate 43 of the swing scroll 40 facing the seal surface 6f is thin (thinned), and the swing-side seal surface 40b is formed on the surface facing the seal surface 6f. Yes.
  • the load on the base plate 43 of the orbiting scroll 40 is small on the outer peripheral side. Even if the thickness of the base plate 43 is reduced, the amount of deformation is small and more effective.
  • FIG. 10 is a schematic side sectional view showing the frame 6 of the scroll compressor 1 according to the fourth embodiment of the present invention.
  • FIG. 11 shows the swing scroll of the scroll compressor 1 according to the fourth embodiment of the present invention.
  • the sealing material 6h is provided in the sealing surface 6f of the seal part 6e.
  • the sealing material 6h is made of, for example, a ring-type resin having good slidability, and is deformed so as to fill the leakage gap with the pressure of the oil to be spilled inside as shown in FIG. Is.

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

Abstract

A scroll compressor (1) is provided with the following: a shell (2) which forms an outer shell and in which in the bottom section thereof an oil reservoir (3a) is formed; an oil pump (3) which is accommodated in the shell (2) and which suctions oil from the oil reservoir (3a); a pressure unit (5) including a fixed scroll (30) that is fixed inside the shell (2) and an oscillating scroll (40) that together with the fixed scroll (30) forms a pressure chamber (5a); a frame (6) which is fixed to the shell (2) and which supports the pressure unit (5); a shaft (7) which is supported by the frame (6) and in which formed therein is an oil channel (7a) in which the oil suctioned by the oil pump (3) flows; a motor (4) which rotationally drives the shaft (7); and an Oldham ring (15) which converts the rotation movement of the shaft (7) to the oscillation movement of the oscillating scroll (40). In the frame (6), formed is an Oldham ring space (15b) for housing the Oldham ring (15). A thrust bearing (6b) for supporting the thrust load of the oscillating scroll (40) is disposed on the inner side of the Oldham ring space (15b), and on the outer side thereof, disposed is a seal (6e) for preventing oil leakage.

Description

スクロール圧縮機Scroll compressor
　本発明は、作動ガスを圧縮するスクロール圧縮機に関するものである。 The present invention relates to a scroll compressor that compresses working gas.
　冷凍機または空調機などに用いられる従来のスクロール圧縮機において、スラスト軸受の摩耗および凝着を抑制したものが知られている（例えば、特許文献１参照）。
　特許文献１に記載のスクロール圧縮機は、固定スクロールと揺動スクロールとを有しており、揺動スクロールは、固定スクロールに対して公転旋回運動（揺動運動）を行う。固定スクロールと揺動スクロールとは、互いに向き合った面に渦巻き状のラップ部が形成された部材であり、双方のラップ部により圧縮室が形成されている。また、揺動スクロールの台板の下面は、スラスト荷重を支持するスラスト面であり、このスラスト面の下側にはスラスト軸受が設けられている。そして、揺動スクロールが揺動することにより、圧縮室の内部容積が変化して、圧縮室に流入した作動ガスを圧縮する。 A conventional scroll compressor used for a refrigerator or an air conditioner is known in which wear and adhesion of a thrust bearing are suppressed (see, for example, Patent Document 1).
The scroll compressor described in Patent Document 1 includes a fixed scroll and a swing scroll, and the swing scroll performs a revolving orbiting motion (swing motion) with respect to the fixed scroll. The fixed scroll and the swing scroll are members in which spiral wrap portions are formed on surfaces facing each other, and a compression chamber is formed by both wrap portions. The lower surface of the base plate of the orbiting scroll is a thrust surface that supports a thrust load, and a thrust bearing is provided below the thrust surface. Then, as the swing scroll swings, the internal volume of the compression chamber changes, and the working gas flowing into the compression chamber is compressed.
　特許文献１では、軸の回転運動を揺動スクロールの揺動運動に変換するオルダムリングを、揺動スクロールの台板の上面側に配置しており、スラスト軸受の面積を広くして面圧を低下させることで、スラスト軸受の摩耗および凝着を抑制している。 In Patent Document 1, an Oldham ring that converts the rotational motion of the shaft into the swing motion of the orbiting scroll is arranged on the upper surface side of the base plate of the orbiting scroll, and the surface pressure is increased by increasing the area of the thrust bearing. By lowering, the wear and adhesion of the thrust bearing are suppressed.
特許第４７４９１３６号公報Japanese Patent No. 4749136
　しかしながら、特許文献１に記載のスクロール圧縮機において、オルダムリングの摺動部への給油が必要であるが、オルダムリングが揺動スクロールの台板の上面側に配置されているため、オルダムリングを潤滑した油は、揺動スクロールのラップ部と固定スクロールのラップ部とにより形成された圧縮室に吸い込まれる。これによって、圧縮機の外に持ち出される油の量（油上がり）が増加し、圧縮機内の油枯渇、オイルセパレータ大型化によるコストアップなどが発生するという課題があった。 However, in the scroll compressor described in Patent Document 1, it is necessary to supply oil to the sliding portion of the Oldham ring. However, since the Oldham ring is arranged on the upper surface side of the base plate of the swing scroll, the Oldham ring is used. The lubricated oil is sucked into a compression chamber formed by the wrap portion of the orbiting scroll and the wrap portion of the fixed scroll. As a result, the amount of oil taken out of the compressor (oil rise) increases, leading to problems such as oil exhaustion in the compressor and cost increase due to an increase in the size of the oil separator.
　本発明は、以上のような課題を解決するためになされたもので、スラスト軸受の摩耗および凝着を抑制しつつ、油上がりの増加を抑制したスクロール圧縮機を提供することを目的としている。 The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a scroll compressor that suppresses an increase in oil rising while suppressing wear and adhesion of a thrust bearing.
　本発明に係るスクロール圧縮機は、外殻を構成し、下部に油溜りが形成されたシェルと、前記シェルに収容され、前記油溜りから油を吸い上げる油ポンプと、前記シェルの内部に固定された固定スクロールと、前記固定スクロールと共に作動ガスを圧縮する圧縮室を形成する揺動スクロールと、を有する圧縮部と、前記シェルに固定され、前記圧縮部を支持するフレームと、前記フレームに支持され、前記油ポンプに吸い上げられた油が流通する油通路が内部に形成された軸部と、前記軸部を回転駆動させるモータと、前記軸部の回転運動を前記揺動スクロールの揺動運動に変換するオルダムリングと、を備え、前記フレームは、前記オルダムリングを収納するオルダムリング空間が形成されており、前記オルダムリング空間の内側には、前記揺動スクロールのスラスト荷重を支持するスラスト軸受が設けられており、前記オルダムリング空間の外側には、油の漏れを防ぐシール部が設けられているものである。 A scroll compressor according to the present invention comprises an outer shell, an oil reservoir formed in a lower portion, an oil pump housed in the shell and sucking up oil from the oil reservoir, and fixed to the inside of the shell. A fixed scroll, a swing scroll that forms a compression chamber that compresses the working gas together with the fixed scroll, a frame fixed to the shell and supporting the compression unit, and supported by the frame. A shaft part in which an oil passage through which oil sucked up by the oil pump flows is formed, a motor that rotationally drives the shaft part, and a rotational movement of the shaft part to a rocking movement of the rocking scroll An Oldham ring to be converted, and the frame is formed with an Oldham ring space for accommodating the Oldham ring, and inside the Oldham ring space, Thrust bearing is provided for supporting the thrust load of KiYurado scroll, on the outside of the Oldham ring space, in which the sealing portion for preventing leakage of oil is provided.
　本発明に係るスクロール圧縮機によれば、スラスト軸受をオルダムリング空間の内側に配置することで、スラスト荷重による揺動スクロールの台板の変形量を抑制することができる。そして、微小なテーパ状の隙間を持った、揺動スクロールのスラスト面とフレームのスラスト軸受との間で油膜が形成されるため、小さなスラスト面積であっても、良好な摺動特性を得ることができ、スラスト軸受での摺動による摩耗および凝着を抑制することができる。また、オルダムリング空間の外側にシール部を設けることで、オルダムリングを潤滑した油がシール部の内側に閉じ込められるため、油が圧縮室に吸入され、油上がりの増加を抑制することができる。 According to the scroll compressor according to the present invention, the amount of deformation of the base plate of the orbiting scroll due to the thrust load can be suppressed by disposing the thrust bearing inside the Oldham ring space. And since an oil film is formed between the thrust surface of the orbiting scroll and the thrust bearing of the frame with a small taper gap, good sliding characteristics can be obtained even with a small thrust area. Wear and adhesion due to sliding in the thrust bearing can be suppressed. Further, by providing the seal portion outside the Oldham ring space, the oil that lubricated the Oldham ring is confined inside the seal portion, so that the oil is sucked into the compression chamber, and an increase in oil rising can be suppressed.
本発明の実施の形態１に係るスクロール圧縮機の軸方向断面模式図である。It is an axial cross-sectional schematic diagram of the scroll compressor which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係るスクロール圧縮機のオルダムリングを示す上面図である。It is a top view which shows the Oldham ring of the scroll compressor which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係るスクロール圧縮機の揺動スクロールを示す下面図である。It is a bottom view which shows the rocking scroll of the scroll compressor which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係るスクロール圧縮機のフレームを示す上面図である。It is a top view which shows the flame | frame of the scroll compressor which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係るスクロール圧縮機のフレームを示す側断面模式図である。It is a side cross-sectional schematic diagram which shows the flame | frame of the scroll compressor which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係るスクロール圧縮機の揺動スクロールを示す軸方向断面模式図である。It is an axial cross-sectional schematic diagram which shows the rocking | fluctuation scroll of the scroll compressor which concerns on Embodiment 1 of this invention. 従来のスクロール圧縮機の揺動スクロールを示す軸方向断面模式図である。It is an axial cross-sectional schematic diagram which shows the rocking | fluctuating scroll of the conventional scroll compressor. 本発明の実施の形態２に係るスクロール圧縮機のフレームを示す側断面模式図である。It is a cross-sectional schematic diagram which shows the flame | frame of the scroll compressor which concerns on Embodiment 2 of this invention. 本発明の実施の形態３に係るスクロール圧縮機の揺動スクロールを示す軸方向断面模式図である。It is an axial cross-sectional schematic diagram which shows the rocking | fluctuation scroll of the scroll compressor which concerns on Embodiment 3 of this invention. 本発明の実施の形態４に係るスクロール圧縮機のフレームを示す側断面模式図である。It is a cross-sectional schematic diagram which shows the flame | frame of the scroll compressor which concerns on Embodiment 4 of this invention. 本発明の実施の形態４に係るスクロール圧縮機の揺動スクロールを示す軸方向断面模式図である。It is an axial cross-sectional schematic diagram which shows the rocking | fluctuation scroll of the scroll compressor which concerns on Embodiment 4 of this invention.
　以下、本発明の実施の形態を図面に基づいて説明する。なお、以下に説明する実施の形態によって本発明が限定されるものではない。また、以下の図面では各構成部材の大きさの関係が実際のものとは異なる場合がある。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments described below. Moreover, in the following drawings, the relationship of the size of each component may be different from the actual one.
　実施の形態１．
　図１は、本発明の実施の形態１に係るスクロール圧縮機１の軸方向断面模式図である。
　以下、図１に基づいて、スクロール圧縮機１について説明する。
　スクロール圧縮機１は、冷凍サイクルを循環する冷媒を吸入して圧縮し、高温高圧の状態にして吐出するものである。スクロール圧縮機１は、シェル２と、油ポンプ３と、モータ４と、圧縮部５と、フレーム６と、軸部７と、を有している。さらに、スクロール圧縮機１は、吸入管１１と、吐出管１２と、吐出チャンバ１３と、マフラー１４と、オルダムリング１５と、スライダ１６と、スリーブ１７と、第１のバランサ１８と、第２のバランサ１９と、サブフレーム２０と、排油パイプ２１と、を有している。 Embodiment 1 FIG.
FIG. 1 is a schematic axial sectional view of a scroll compressor 1 according to Embodiment 1 of the present invention.
Hereinafter, the scroll compressor 1 will be described with reference to FIG.
The scroll compressor 1 sucks and compresses the refrigerant circulating in the refrigeration cycle, and discharges it in a high-temperature and high-pressure state. The scroll compressor 1 includes a shell 2, an oil pump 3, a motor 4, a compression part 5, a frame 6, and a shaft part 7. Further, the scroll compressor 1 includes a suction pipe 11, a discharge pipe 12, a discharge chamber 13, a muffler 14, an Oldham ring 15, a slider 16, a sleeve 17, a first balancer 18, and a second balancer. The balancer 19, the subframe 20, and the oil drain pipe 21 are provided.
　シェル２は、スクロール圧縮機１の外殻を構成し、下部に油溜り３ａが形成されたものである。また、シェル２は、例えば有底円筒状をなしており、ドーム状のアッパーシェル２ａによって上部が塞がれている。また、シェル２は、ロアーシェル２ｂに載置されている。 The shell 2 constitutes the outer shell of the scroll compressor 1 and has an oil sump 3a formed in the lower part. The shell 2 has, for example, a bottomed cylindrical shape, and the upper portion is closed by a dome-shaped upper shell 2a. The shell 2 is placed on the lower shell 2b.
　油ポンプ３は、シェル２に収容され、油溜り３ａから油を吸い上げるものである。この油ポンプ３は、シェル２の下部に設けられている。そして、油ポンプ３は、油溜り３ａから吸い上げた油を、スクロール圧縮機１の内部の軸受部を潤滑する。また、揺動軸受を潤滑した後の油はフレーム６の内部空間６ｄ（後述する図４参照）に蓄えられた後、スラスト軸受６ｂに設けられた放射状の給油溝６ｃを通り、オルダムリング空間１５ｂに流れてオルダムリング１５を潤滑する。オルダムリング空間１５ｂには、排油パイプ２１が設けてあり、排油パイプ２１を通って油は油溜り３ａに戻される。 The oil pump 3 is accommodated in the shell 2 and sucks up oil from the oil sump 3a. The oil pump 3 is provided at the lower part of the shell 2. And the oil pump 3 lubricates the bearing part inside the scroll compressor 1 with the oil sucked up from the oil reservoir 3a. The oil after lubricating the oscillating bearing is stored in an internal space 6d (see FIG. 4 described later) of the frame 6, and then passes through the radial oil supply groove 6c provided in the thrust bearing 6b, and the Oldham ring space 15b. To lubricate the Oldham ring 15. The Oldham ring space 15 b is provided with a drain oil pipe 21, and the oil is returned to the oil sump 3 a through the drain oil pipe 21.
　モータ４は、シェル２の内部に設けられ、例えばフレーム６とサブフレーム２０との間に設置されており、軸部７を回転させるものである。モータ４は、ロータ４ａとステータ４ｂとを有している。ロータ４ａは、ステータ４ｂの内周側に設けられており、軸部７に取り付けられている。そして、ロータ４ａは、自らが回転することにより、軸部７を回転させるものである。ステータ４ｂは、インバータ（図示せず）から供給された電力によって、ロータ４ａを回転させるものである。 The motor 4 is provided inside the shell 2 and is installed, for example, between the frame 6 and the sub-frame 20 and rotates the shaft portion 7. The motor 4 has a rotor 4a and a stator 4b. The rotor 4 a is provided on the inner peripheral side of the stator 4 b and is attached to the shaft portion 7. And the rotor 4a rotates the axial part 7 by rotating itself. The stator 4b rotates the rotor 4a with electric power supplied from an inverter (not shown).
　圧縮部５は、シェル２の内部に設けられ、モータ４によって駆動して作動ガスを圧縮するものである。圧縮部５は、固定スクロール３０と揺動スクロール４０とを有している。固定スクロール３０は、シェル２の内部に固定されており、圧縮された作動ガスを吐出チャンバ１３に流出させるものである。 The compression unit 5 is provided inside the shell 2 and is driven by the motor 4 to compress the working gas. The compression unit 5 includes a fixed scroll 30 and a swing scroll 40. The fixed scroll 30 is fixed inside the shell 2 and causes the compressed working gas to flow out into the discharge chamber 13.
　揺動スクロール４０は、固定スクロール３０に対して公転旋回運動（揺動運動）を行い、オルダムリング１５によって自転運動が規制されている。固定スクロール３０と揺動スクロール４０とは、夫々互いに向き合った面に渦巻き状のラップ部３１とラップ部４１とが形成された部材であり、固定スクロール３０のラップ部３１と揺動スクロール４０のラップ部４１とが噛み合った空間に圧縮室５ａが形成されている。揺動スクロール４０が軸部７によって揺動運動され、形成された圧縮室５ａにおいて作動ガスが圧縮される。 The orbiting scroll 40 performs a revolving orbiting motion (oscillating motion) with respect to the fixed scroll 30, and the rotation motion is regulated by the Oldham ring 15. The fixed scroll 30 and the swing scroll 40 are members in which spiral wrap portions 31 and a wrap portion 41 are formed on surfaces facing each other. The wrap portion 31 of the fixed scroll 30 and the wrap portion of the swing scroll 40 are provided. A compression chamber 5a is formed in a space where the portion 41 is engaged. The swing scroll 40 is swung by the shaft portion 7, and the working gas is compressed in the formed compression chamber 5a.
　フレーム６は、シェル２に固定され、圧縮部５を収容するものであり、例えば主軸受８ａを介して軸部７を回転自在に支持している。フレーム６には、吸入ポート６ａが形成されており、作動ガスは、吸入ポート６ａを通って圧縮部５に流入する。軸部７は、フレーム６に支持され、油ポンプ３に吸い上げられた油が流通する油通路７ａが内部に形成されており、モータ４と圧縮部５とを接続してモータ４の回転力を圧縮部５に伝達するものである。 The frame 6 is fixed to the shell 2 and accommodates the compression portion 5, and for example, rotatably supports the shaft portion 7 via a main bearing 8a. A suction port 6a is formed in the frame 6, and the working gas flows into the compression unit 5 through the suction port 6a. The shaft portion 7 is supported by the frame 6 and has an oil passage 7a through which oil sucked up by the oil pump 3 flows. The shaft portion 7 connects the motor 4 and the compression portion 5 to increase the rotational force of the motor 4. This is transmitted to the compression unit 5.
　吸入管１１は、シェル２の側部に設けられており、作動ガスをシェル２の内部に吸入する管である。吐出管１２は、シェル２の上部に設けられており、作動ガスをシェル２の外部に吐出する管である。吐出チャンバ１３は、圧縮部５の上部に設けられており、圧縮部５から流入した作動ガスを収容するものである。マフラー１４は、吐出チャンバ１３の上方に設けられており、吐出チャンバ１３から吐出された作動ガスの脈動を抑えるものである。 The suction pipe 11 is provided on the side of the shell 2 and sucks the working gas into the shell 2. The discharge pipe 12 is provided on the upper part of the shell 2 and discharges the working gas to the outside of the shell 2. The discharge chamber 13 is provided in the upper part of the compression part 5, and accommodates the working gas which flowed in from the compression part 5. The muffler 14 is provided above the discharge chamber 13 and suppresses pulsation of the working gas discharged from the discharge chamber 13.
　図２は、本発明の実施の形態１に係るスクロール圧縮機１のオルダムリング１５を示す上面図であり、図３は、本発明の実施の形態１に係るスクロール圧縮機１の揺動スクロール４０を示す下面図である。
　オルダムリング１５は、図２に示すように揺動スクロール４０に取り付けられた環状の部材であり、揺動スクロール４０の自転運動を規制するものである。オルダムリング１５は、オルダム爪１５ｃを有し、図３に示す揺動スクロール４０の台板４３の下面に形成されたオルダム溝１５ａに嵌入されている。 FIG. 2 is a top view showing the Oldham ring 15 of the scroll compressor 1 according to the first embodiment of the present invention, and FIG. 3 is a swing scroll 40 of the scroll compressor 1 according to the first embodiment of the present invention. FIG.
The Oldham ring 15 is an annular member attached to the orbiting scroll 40 as shown in FIG. 2, and restricts the rotational movement of the orbiting scroll 40. The Oldham ring 15 has an Oldham claw 15c and is fitted into an Oldham groove 15a formed on the lower surface of the base plate 43 of the swing scroll 40 shown in FIG.
　スライダ１６は、軸部７の上部の外周面に取り付けられた筒状の部材であり、揺動スクロール４０の下部の内面に位置している。すなわち、揺動スクロール４０は、スライダ１６を介して軸部７に取り付けられており、軸部７の回転に伴って揺動スクロール４０も回転する。なお、揺動スクロール４０とスライダ１６との間には、揺動軸受８ｃが設けられている。スリーブ１７は、フレーム６と主軸受８ａとの間に設けられた筒状の部材であり、フレーム６と軸部７との傾斜を吸収するものである。 The slider 16 is a cylindrical member attached to the outer peripheral surface of the upper portion of the shaft portion 7, and is located on the inner surface of the lower portion of the swing scroll 40. That is, the orbiting scroll 40 is attached to the shaft portion 7 via the slider 16, and the orbiting scroll 40 rotates as the shaft portion 7 rotates. A rocking bearing 8 c is provided between the rocking scroll 40 and the slider 16. The sleeve 17 is a cylindrical member provided between the frame 6 and the main bearing 8 a and absorbs the inclination between the frame 6 and the shaft portion 7.
　第１のバランサ１８は、軸部７に取り付けられており、フレーム６とロータ４ａとの間に位置している。第１のバランサ１８は、揺動スクロール４０およびスライダ１６によって生じるアンバランスを相殺するものである。なお、第１のバランサ１８は、バランサカバー１８ａに収容されている。また、第２のバランサ１９は、軸部７に取り付けられており、ロータ４ａとサブフレーム２０との間に位置し、ロータ４ａの下面に取り付けられている。第２のバランサ１９は、揺動スクロール４０およびスライダ１６によって生じるアンバランスを相殺するものである。 The first balancer 18 is attached to the shaft 7 and is located between the frame 6 and the rotor 4a. The first balancer 18 cancels the imbalance caused by the orbiting scroll 40 and the slider 16. The first balancer 18 is accommodated in the balancer cover 18a. The second balancer 19 is attached to the shaft portion 7, is located between the rotor 4 a and the sub frame 20, and is attached to the lower surface of the rotor 4 a. The second balancer 19 cancels the imbalance caused by the orbiting scroll 40 and the slider 16.
　サブフレーム２０は、シェル２の内部におけるモータ４の下方に設けられ、副軸受８ｂを介して軸部７を回転自在に支持するものである。排油パイプ２１は、フレーム６と揺動スクロール４０との間の空間と、フレーム６とサブフレーム２０との間の空間とを接続する管である。排油パイプ２１は、フレーム６と揺動スクロール４０との間の空間に流通する油のうち、過剰な油を、フレーム６とサブフレーム２０との間の空間に流出させる。フレーム６とサブフレーム２０との間の空間に流出した油は、サブフレーム２０を通過して油溜り３ａに戻る。 The sub-frame 20 is provided below the motor 4 inside the shell 2 and rotatably supports the shaft portion 7 via the sub-bearing 8b. The oil drain pipe 21 is a pipe that connects the space between the frame 6 and the swing scroll 40 and the space between the frame 6 and the subframe 20. The oil drain pipe 21 causes excess oil out of the oil flowing in the space between the frame 6 and the swing scroll 40 to flow into the space between the frame 6 and the sub-frame 20. The oil that has flowed into the space between the frame 6 and the subframe 20 passes through the subframe 20 and returns to the oil sump 3a.
　次に、圧縮部５について詳細に説明する。
　圧縮部５は、上記の通り、固定スクロール３０と揺動スクロール４０とを有している。固定スクロール３０は、シェル２の内部に固定され、外周縁部がフレーム６の上部に載置されている。揺動スクロール４０は、下面にスラスト荷重を支持するスラスト面４０ａが設けられており、フレーム６のスラスト面４０ａと対向する面の内、内周側にはスラスト荷重を支持するスラスト軸受６ｂが設けられている。 Next, the compression unit 5 will be described in detail.
The compression unit 5 includes the fixed scroll 30 and the swing scroll 40 as described above. The fixed scroll 30 is fixed inside the shell 2, and the outer peripheral edge portion is placed on the upper portion of the frame 6. The rocking scroll 40 is provided with a thrust surface 40a for supporting a thrust load on the lower surface, and a thrust bearing 6b for supporting the thrust load is provided on the inner peripheral side of the surface of the frame 6 facing the thrust surface 40a. It has been.
　スラスト軸受６ｂは、例えば熱処理がされていたり、給油溝６ｃが設けられていたりして、良好な摺動性が確保されている。摺動性の良い別部材をスラスト軸受６ｂとして配置しても良い。スラスト軸受６ｂの外周にはオルダムリング空間１５ｂが設けられており、オルダムリング空間１５ｂにはオルダムリング１５が収納される。オルダムリング空間１５ｂの外周には、シール部６ｅが設けられており、その上面にはシール面６ｆが形成されている。シール部６ｅと、シール面６ｆに対向する揺動スクロール４０の台板４３とで、オルダムリング空間１５ｂから油が外周に流れ出て圧縮室５ａに吸入されることを抑制している（後述する図４参照）。 The thrust bearing 6b is heat-treated or provided with an oil supply groove 6c, for example, to ensure good slidability. Another member having good slidability may be disposed as the thrust bearing 6b. An Oldham ring space 15b is provided on the outer periphery of the thrust bearing 6b, and the Oldham ring 15 is accommodated in the Oldham ring space 15b. A seal portion 6e is provided on the outer periphery of the Oldham ring space 15b, and a seal surface 6f is formed on the upper surface thereof. The seal portion 6e and the base plate 43 of the orbiting scroll 40 facing the seal surface 6f suppress oil from flowing out from the Oldham ring space 15b to the outer periphery and being sucked into the compression chamber 5a (a later-described figure). 4).
　図４は、本発明の実施の形態１に係るスクロール圧縮機１のフレーム６を示す上面図であり、図５は、本発明の実施の形態１に係るスクロール圧縮機１のフレーム６を示す側断面模式図である。
　フレーム６内にはスラスト軸受６ｂが設けられており、その外周側には、油が外周に漏れるのを防ぐためのシール部６ｅが設けられており、スラスト軸受６ｂとシール部６ｅとの間には、オルダムリング空間１５ｂが形成されている。そして、そのオルダムリング空間１５ｂに、オルダムリング空間１５ｂ内で往復運動するオルダムリング１５が収納されている。 FIG. 4 is a top view showing frame 6 of scroll compressor 1 according to Embodiment 1 of the present invention, and FIG. 5 is a side showing frame 6 of scroll compressor 1 according to Embodiment 1 of the present invention. It is a cross-sectional schematic diagram.
A thrust bearing 6b is provided in the frame 6, and a seal portion 6e for preventing oil from leaking to the outer periphery is provided on the outer peripheral side, and between the thrust bearing 6b and the seal portion 6e. The Oldham ring space 15b is formed. The Oldham ring 15 that reciprocates in the Oldham ring space 15b is accommodated in the Oldham ring space 15b.
　ここで、スクロール圧縮機１の回転中心からスラスト軸受６ｂの外周面までの距離をＲｔｈｏ、スクロール圧縮機１の回転中心からシール部６ｅの内周面までの距離をＲｓｅａｌｉとした時、Ｒｔｈｏ＜r＜Ｒｓｅａｌｉの範囲にオルダムリング１５が収納されることになる。 Here, when the distance to the inner peripheral surface of the seal portion 6e was R Seali the distance from the rotation center of the scroll compressor 1 to the outer peripheral surface of the thrust bearing 6b R tho, from the rotational center of the scroll compressor 1, R The Oldham ring 15 is accommodated in the range of th <r <R seal .
　スラスト軸受６ｂには、給油溝６ｃが放射状に設けられており、スラスト軸受６ｂよりも内側の内部空間６ｄに蓄えられた油が給油溝６ｃを通ることで、スラスト軸受６ｂおよびオルダムリング１５の潤滑を行う。
　フレーム６には、オルダムリング空間１５ｂと連通した排油穴１５ｅが形成されており、オルダムリング空間１５ｂに溜まった油は、その排油穴１５ｅを通って排油パイプ２１から排出される。 The thrust bearing 6b is provided with oil supply grooves 6c radially, and the oil stored in the internal space 6d inside the thrust bearing 6b passes through the oil supply groove 6c, whereby the thrust bearing 6b and the Oldham ring 15 are lubricated. I do.
An oil drain hole 15e communicating with the Oldham ring space 15b is formed in the frame 6, and oil accumulated in the Oldham ring space 15b is discharged from the oil drain pipe 21 through the oil drain hole 15e.
　スラスト軸受６ｂの上面とシール部６ｅのシール面６ｆとは同一平面上に存在する。揺動スクロール４０の台板４３の半径をＲｏｓ、公転半径をＲｒとした時、Ｒｏｓ－(Ｒｒ+Ｒｓｅａｌ)＞０の寸法関係にすることで、揺動スクロール４０の台板４３の下面と、フレーム６のシール部６ｅのシール面６ｆとが揺動スクロール４０のクランク角に拠らず重なり、油のシール性を確保することができる。 The upper surface of the thrust bearing 6b and the seal surface 6f of the seal portion 6e are on the same plane. When the radius of the base plate 43 of the orbiting scroll 40 is R os and the revolution radius is R r , the base plate of the orbiting scroll 40 is set to have a dimensional relationship of R os − (R r + R seal )> 0. The lower surface of 43 and the seal surface 6f of the seal portion 6e of the frame 6 overlap without depending on the crank angle of the orbiting scroll 40, and the oil sealability can be ensured.
　図６は、本発明の実施の形態１に係るスクロール圧縮機１の揺動スクロール４０を示す軸方向断面模式図である。図７は、従来のスクロール圧縮機の揺動スクロール１４０を示す軸方向断面模式図である。
　図６に示す本実施の形態１に係るスクロール圧縮機１では、図７に示す従来のスクロール圧縮機と比較して、スラスト荷重の支持スパンＤが短い。ここで、スクロール圧縮機１の回転中心からスラスト軸受６ｂの内周面までの距離をＲｔｈｉとすると、Ｄ＝２Ｒｔｈｉである。 FIG. 6 is a schematic axial sectional view showing the orbiting scroll 40 of the scroll compressor 1 according to Embodiment 1 of the present invention. FIG. 7 is a schematic axial sectional view showing a swing scroll 140 of a conventional scroll compressor.
In the scroll compressor 1 according to the first embodiment shown in FIG. 6, the support span D of the thrust load is shorter than that of the conventional scroll compressor shown in FIG. Here, if the distance from the rotation center of the scroll compressor 1 to the inner peripheral surface of the thrust bearing 6b is R thi , D = 2R thi .
　本実施の形態１では、スラスト軸受６ｂをオルダムリング空間１５ｂの内側に配置することで、従来に比べてスラスト荷重の支持スパンＤが短いため、スラスト荷重による揺動スクロール４０の台板４３の変形を抑制することができる。そして、微小なテーパ状の隙間を持った、揺動スクロール４０のスラスト面４０ａとスラスト軸受６ｂとの間に、楔効果および絞り膜効果により大きな油膜圧力が発生し、油膜が形成されるため、小さなスラスト面積であっても、良好な摺動特性を得ることができ、スラスト軸受６ｂでの摺動による摩耗および凝着を抑制することができる。その結果、スラスト軸受６ｂの信頼性を改善することができる。
　また、オルダムリング空間１５ｂの外側にシール部６ｅを設けることで、オルダムリング１５を潤滑した油がシール部６ｅの内側に閉じ込められるため、油が圧縮室５ａに吸入され、油上がりの増加を抑制することができる。 In the first embodiment, the thrust bearing 6b is arranged inside the Oldham ring space 15b, so that the support span D of the thrust load is shorter than the conventional one. Therefore, the base plate 43 of the orbiting scroll 40 is deformed by the thrust load. Can be suppressed. Since a large oil film pressure is generated by the wedge effect and the throttle film effect between the thrust surface 40a of the orbiting scroll 40 and the thrust bearing 6b having a small tapered gap, an oil film is formed. Even with a small thrust area, good sliding characteristics can be obtained, and wear and adhesion due to sliding on the thrust bearing 6b can be suppressed. As a result, the reliability of the thrust bearing 6b can be improved.
Further, by providing the seal portion 6e outside the Oldham ring space 15b, the oil that lubricated the Oldham ring 15 is confined inside the seal portion 6e, so that the oil is sucked into the compression chamber 5a and the increase in oil rise is suppressed. can do.
　なお、図７の構成の場合でも、揺動スクロール１４０の台板１４３を厚くすることで、台板１４３の撓み量を抑制することはできるが、この場合、揺動スクロール１４０の重量が増加し、主軸受、副軸受、スクロールラップ面の荷重増加という問題が発生する。 Even in the case of the configuration of FIG. 7, the amount of bending of the base plate 143 can be suppressed by increasing the thickness of the base plate 143 of the swing scroll 140, but in this case, the weight of the swing scroll 140 increases. The problem of increased load on the main bearing, sub-bearing, and scroll wrap surface occurs.
　また、スラスト軸受６ｂの上面の面積について、油膜圧力が主に発生するのはスラスト軸受６ｂの内周側であり、スラスト軸受６ｂの外周側の面積を削減しても、スラスト軸受６ｂの信頼性への影響は小さい。 Further, regarding the area of the upper surface of the thrust bearing 6b, the oil film pressure is mainly generated on the inner peripheral side of the thrust bearing 6b. Even if the area on the outer peripheral side of the thrust bearing 6b is reduced, the reliability of the thrust bearing 6b is increased. The impact on is small.
　実施の形態２．
　以下、本発明の実施の形態２について説明するが、実施の形態１と重複するものについては（一部の）説明を省略し、実施の形態１と同じ部分または相当する部分には同じ符号を付す。
　図８は、本発明の実施の形態２に係るスクロール圧縮機１のフレーム６を示す側断面模式図である。 Embodiment 2. FIG.
Hereinafter, the second embodiment of the present invention will be described. However, the description of (a part of) the same as that of the first embodiment is omitted, and the same reference numerals are given to the same or corresponding parts as those of the first embodiment. Attached.
FIG. 8 is a schematic side sectional view showing the frame 6 of the scroll compressor 1 according to Embodiment 2 of the present invention.
　本実施の形態２では、スラスト軸受６ｂの上部が、その上部以外の部分（およびフレーム６）とは別部材６ｇで形成されている。ここで、別部材６ｇは、例えば摺動性の高い合金、樹脂で作られたリング型の軸受メタルなどであり、スラスト軸受６ｂの上部を、その上部以外の部分（およびフレーム６）とは別部材６ｇで形成することにより、耐摩耗性、耐焼付き性をさらに改善することができる。スラスト軸受６ｂの上面は確実に、シール部６ｅのシール面６ｆよりも高くする必要があり、シール部６ｅのシール面６ｆからスラスト軸受６ｂの上面までの高さｈ１を０～５０μｍに設定することで、良好なシール性を得ることができる。 In the second embodiment, the upper portion of the thrust bearing 6b is formed of a member 6g separate from the portion other than the upper portion (and the frame 6). Here, the separate member 6g is, for example, a ring-type bearing metal made of a highly slidable alloy or resin, and the upper portion of the thrust bearing 6b is different from the portions other than the upper portion (and the frame 6). By forming the member 6g, the wear resistance and seizure resistance can be further improved. The upper surface of the thrust bearing 6b must surely be higher than the seal surface 6f of the seal portion 6e, and the height h1 from the seal surface 6f of the seal portion 6e to the upper surface of the thrust bearing 6b should be set to 0 to 50 μm. Thus, good sealing properties can be obtained.
　実施の形態３．
　以下、本発明の実施の形態３について説明するが、実施の形態１および２と重複するものについては（一部の）説明を省略し、実施の形態１および２と同じ部分または相当する部分には同じ符号を付す。
　図９は、本発明の実施の形態３に係るスクロール圧縮機１の揺動スクロール４０を示す軸方向断面模式図である。 Embodiment 3 FIG.
Hereinafter, the third embodiment of the present invention will be described, but the description of (part of) the same parts as those of the first and second embodiments will be omitted, and the same or corresponding parts as those of the first and second embodiments will be omitted. Are given the same symbols.
FIG. 9 is a schematic axial sectional view showing the orbiting scroll 40 of the scroll compressor 1 according to Embodiment 3 of the present invention.
　本実施の形態３では、フレーム６のスラスト軸受６ｂよりもシール部６ｅが高くなっている。つまり、スラスト軸受６ｂの上面よりも、シール部６ｅのシール面６ｆが上側に配置されている。そして、揺動スクロール４０の台板４３の、シール面６ｆと対向する部分の肉厚が薄く（薄肉化）されており、シール面６ｆと対向する面に揺動側シール面４０ｂが形成されている。シール面６ｆと揺動側シール面４０ｂとの隙間ｈ２を０～５０μｍ程度に設定することで、油のシール性を確保する。 In the third embodiment, the seal portion 6e is higher than the thrust bearing 6b of the frame 6. That is, the seal surface 6f of the seal portion 6e is arranged on the upper side of the upper surface of the thrust bearing 6b. The thickness of the portion of the base plate 43 of the swing scroll 40 facing the seal surface 6f is thin (thinned), and the swing-side seal surface 40b is formed on the surface facing the seal surface 6f. Yes. By setting the gap h2 between the seal surface 6f and the oscillating side seal surface 40b to about 0 to 50 μm, the oil sealability is ensured.
　スクロール圧縮機１のように、揺動スクロール４０の外周側から作動ガスを吸入し、内周側で圧縮する圧縮機においては、外周側は揺動スクロール４０の台板４３にかかる荷重が小さいため、台板４３の肉厚を薄くしても変形量が小さく、より効果的である。 In a compressor that draws working gas from the outer peripheral side of the orbiting scroll 40 and compresses on the inner peripheral side like the scroll compressor 1, the load on the base plate 43 of the orbiting scroll 40 is small on the outer peripheral side. Even if the thickness of the base plate 43 is reduced, the amount of deformation is small and more effective.
　実施の形態４．
　以下、本発明の実施の形態４について説明するが、実施の形態１～３と重複するものについては（一部の）説明を省略し、実施の形態１～３と同じ部分または相当する部分には同じ符号を付す。
　図１０は、本発明の実施の形態４に係るスクロール圧縮機１のフレーム６を示す側断面模式図であり、図１１は、本発明の実施の形態４に係るスクロール圧縮機１の揺動スクロール４０を示す軸方向断面模式図である。 Embodiment 4 FIG.
Hereinafter, the fourth embodiment of the present invention will be described. However, the description of the same parts as those of the first to third embodiments will be omitted, and the same or corresponding parts as those of the first to third embodiments will be omitted. Are given the same symbols.
FIG. 10 is a schematic side sectional view showing the frame 6 of the scroll compressor 1 according to the fourth embodiment of the present invention. FIG. 11 shows the swing scroll of the scroll compressor 1 according to the fourth embodiment of the present invention. FIG.
　本実施の形態４では、図１０に示すように、シール部６ｅのシール面６ｆにシール材６ｈが設けられている。ここで、シール材６ｈは、例えば摺動性のよいリング型の樹脂製のものであり、図１１に示すように、内側の流出しようとする油の圧力で、漏れ隙間を埋めるように変形するものである。このようにシール材６ｈを設けることで、油のシール性を向上させることができる。 In this Embodiment 4, as shown in FIG. 10, the sealing material 6h is provided in the sealing surface 6f of the seal part 6e. Here, the sealing material 6h is made of, for example, a ring-type resin having good slidability, and is deformed so as to fill the leakage gap with the pressure of the oil to be spilled inside as shown in FIG. Is. By providing the sealing material 6h in this way, the oil sealing performance can be improved.
　１　スクロール圧縮機、２　シェル、２ａ　アッパーシェル、２ｂ　ロアーシェル、３　油ポンプ、３ａ　油溜り、４　モータ、４ａ　ロータ、４ｂ　ステータ、５　圧縮部、５ａ　圧縮室、６　フレーム、６ａ　吸入ポート、６ｂ　スラスト軸受、６ｃ　給油溝、６ｄ　内部空間、６ｅ　シール部、６ｆ　シール面、６ｇ　別部材、６ｈ　シール材、７　軸部、７ａ　油通路、８ａ　主軸受、８ｂ　副軸受、８ｃ　揺動軸受、１１　吸入管、１２　吐出管、１３　吐出チャンバ、１４　マフラー、１５　オルダムリング、１５ａ　オルダム溝、１５ｂ　オルダムリング空間、１５ｃ　オルダム爪、１５ｅ　排油穴、１６　スライダ、１７　スリーブ、１８　第１のバランサ、１８ａ　バランサカバー、１９　第２のバランサ、２０　サブフレーム、２１　排油パイプ、３０　固定スクロール、３１　ラップ部、４０　揺動スクロール、４０ａ　スラスト面、４０ｂ　揺動側シール面、４１　ラップ部、４３　台板、１０６　フレーム、１０６ｂ　スラスト軸受、１１５ｂ　オルダムリング空間、１４０　揺動スクロール、１４３　台板。 1 scroll compressor, 2 shell, 2a upper shell, 2b lower shell, 3 oil pump, 3a oil sump, 4 motor, 4a rotor, 4b stator, 5 compression section, 5a compression chamber, 6 frame, 6a suction port, 6b thrust bearing 6c oil supply groove, 6d internal space, 6e seal part, 6f seal surface, 6g separate member, 6h seal material, 7 shaft part, 7a oil passage, 8a main bearing, 8b sub-bearing, 8c swing bearing, 11 suction pipe, 12 discharge pipe, 13 discharge chamber, 14 muffler, 15 Oldham ring, 15a Oldham groove, 15b Oldham ring space, 15c Oldham claw, 15e oil drain hole, 16 slider, 17 sleeve, 18 first balancer, 18a balancer cover, 19 Second balancer, 20 sub Rame, 21 oil drain pipe, 30 fixed scroll, 31 lap part, 40 rocking scroll, 40a thrust surface, 40b rocking side seal surface, 41 lap part, 43 base plate, 106 frame, 106b thrust bearing, 115b Oldham ring space 140 swing scroll, 143 base plate.

Claims (6)

  1. 　外殻を構成し、下部に油溜りが形成されたシェルと、
    　前記シェルに収容され、前記油溜りから油を吸い上げる油ポンプと、
    　前記シェルの内部に固定された固定スクロールと、前記固定スクロールと共に作動ガスを圧縮する圧縮室を形成する揺動スクロールと、を有する圧縮部と、
    　前記シェルに固定され、前記圧縮部を支持するフレームと、
    　前記フレームに支持され、前記油ポンプに吸い上げられた油が流通する油通路が内部に形成された軸部と、
    　前記軸部を回転駆動させるモータと、
    　前記軸部の回転運動を前記揺動スクロールの揺動運動に変換するオルダムリングと、を備え、
    　前記フレームは、
    　前記オルダムリングを収納するオルダムリング空間が形成されており、
    　前記オルダムリング空間の内側には、前記揺動スクロールのスラスト荷重を支持するスラスト軸受が設けられており、前記オルダムリング空間の外側には、油の漏れを防ぐシール部が設けられている
    　スクロール圧縮機。     A shell that forms an outer shell and has an oil sump formed at the bottom;
    An oil pump housed in the shell and sucking up oil from the oil reservoir;
    A compression part having a fixed scroll fixed inside the shell, and a swinging scroll that forms a compression chamber for compressing a working gas together with the fixed scroll;
    A frame fixed to the shell and supporting the compression part;
    A shaft part formed in the inside of an oil passage that is supported by the frame and through which oil sucked up by the oil pump flows;
    A motor that rotationally drives the shaft portion;
    An Oldham ring for converting the rotational motion of the shaft portion into the rocking motion of the rocking scroll,
    The frame is
    An Oldham ring space for storing the Oldham ring is formed,
    A thrust bearing that supports the thrust load of the orbiting scroll is provided inside the Oldham ring space, and a seal portion that prevents oil leakage is provided outside the Oldham ring space. Machine.
  2. 　前記スラスト軸受には、前記フレームの内部空間に蓄えられた油が前記オルダムリング空間に流れる給油溝が形成されており、
    　前記フレームには、前記オルダムリング空間と連通した排油穴が形成されている
    　請求項１に記載のスクロール圧縮機。     The thrust bearing is formed with an oil supply groove through which oil stored in the internal space of the frame flows into the Oldham ring space,
    The scroll compressor according to claim 1, wherein an oil drain hole communicating with the Oldham ring space is formed in the frame.
  3. 　前記スラスト軸受の上面は、前記シール部の上面よりも高い
    　請求項１または２に記載のスクロール圧縮機。     The scroll compressor according to claim 1, wherein an upper surface of the thrust bearing is higher than an upper surface of the seal portion.
  4. 　前記スラスト軸受は、上部と該上部以外の部分とが別部材で形成されている
    　請求項１～３のいずれか一項に記載のスクロール圧縮機。     The scroll compressor according to any one of claims 1 to 3, wherein the thrust bearing has an upper portion and a portion other than the upper portion formed of separate members.
  5. 　前記揺動スクロールは、下面が前記フレームと対向する台板を有し、
    　前記スラスト軸受の上面よりも、前記シール部の上面を上側に配置し、前記揺動スクロールの前記台板の前記シール部の上面と対向する部分が薄肉化されている
    　請求項１または２に記載のスクロール圧縮機。     The orbiting scroll has a base plate whose lower surface faces the frame,
    The upper surface of the said seal part is arrange | positioned rather than the upper surface of the said thrust bearing, and the part facing the upper surface of the said seal part of the said base plate of the said rocking scroll is thinned. Scroll compressor.
  6. 　前記シール部の上面にシール材が設けられている
    　請求項１～５のいずれか一項に記載のスクロール圧縮機。     The scroll compressor according to any one of claims 1 to 5, wherein a sealing material is provided on an upper surface of the seal portion.
PCT/JP2015/065437 2015-05-28 2015-05-28 Scroll compressor WO2016189738A1 (en)

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CN111788394A (en) * 2018-03-05 2020-10-16 三菱电机株式会社 Compressor with a compressor housing having a plurality of compressor blades
JPWO2022054174A1 (en) * 2020-09-09 2022-03-17
US11933304B2 (en) 2021-09-02 2024-03-19 Bitzer Kuehlmaschinenbau Gmbh Scroll compressor including hub lubricant passage

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JPH0658274A (en) * 1992-08-06 1994-03-01 Daikin Ind Ltd Scroll compressor
JPH07229490A (en) * 1994-02-18 1995-08-29 Fujitsu General Ltd Scroll compressor

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US4696630A (en) * 1983-09-30 1987-09-29 Kabushiki Kaisha Toshiba Scroll compressor with a thrust reduction mechanism
JPS62199985A (en) * 1986-02-28 1987-09-03 Toshiba Corp Scroll type compressor
JPH0658274A (en) * 1992-08-06 1994-03-01 Daikin Ind Ltd Scroll compressor
JPH07229490A (en) * 1994-02-18 1995-08-29 Fujitsu General Ltd Scroll compressor

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Publication number Priority date Publication date Assignee Title
CN111788394A (en) * 2018-03-05 2020-10-16 三菱电机株式会社 Compressor with a compressor housing having a plurality of compressor blades
JPWO2022054174A1 (en) * 2020-09-09 2022-03-17
WO2022054174A1 (en) * 2020-09-09 2022-03-17 三菱電機株式会社 Scroll compressor
JP7395004B2 (en) 2020-09-09 2023-12-08 三菱電機株式会社 scroll compressor
US11933304B2 (en) 2021-09-02 2024-03-19 Bitzer Kuehlmaschinenbau Gmbh Scroll compressor including hub lubricant passage

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