WO2019044867A1 - スクロール型圧縮機 - Google Patents

スクロール型圧縮機 Download PDF

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Publication number
WO2019044867A1
WO2019044867A1 PCT/JP2018/031857 JP2018031857W WO2019044867A1 WO 2019044867 A1 WO2019044867 A1 WO 2019044867A1 JP 2018031857 W JP2018031857 W JP 2018031857W WO 2019044867 A1 WO2019044867 A1 WO 2019044867A1
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WO
WIPO (PCT)
Prior art keywords
oil
scroll
outer peripheral
compression mechanism
fixed scroll
Prior art date
Application number
PCT/JP2018/031857
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
貞光 塚越
裕暁 岡倉
亮介 井澤
Original Assignee
株式会社ヴァレオジャパン
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社ヴァレオジャパン filed Critical 株式会社ヴァレオジャパン
Priority to JP2019539555A priority Critical patent/JP7075407B2/ja
Priority to CN201880062922.1A priority patent/CN111133197B/zh
Publication of WO2019044867A1 publication Critical patent/WO2019044867A1/ja

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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 can be used for a refrigeration cycle or the like of a vehicle air conditioner.
  • the scroll compressor has a compression mechanism having an end plate, a fixed scroll having a spiral wall provided upright from the end plate, an end plate, and a orbiting scroll having a spiral wall provided upright from the end plate. .
  • a compression chamber formed between the scroll wall of the fixed scroll and the scroll wall of the orbiting scroll moves to the center of the scroll while reducing its volume, thereby compressing the working fluid.
  • lubricating oil is supplied into the compression mechanism.
  • an oil introducing passage is provided which is composed of a hole, a groove or a combination of these located in the lower part of the compression mechanism, particularly the fixed scroll (see, for example, Patent Document 1).
  • an excessive amount of oil is taken in between both scrolls under certain operating conditions, for example, a situation where a large amount of oil is accumulated in the lower part of the compression mechanism, and compression is performed. Oil compression may occur which may result in reduced efficiency or damage to the machine.
  • An object of the present invention is to provide a scroll type compressor capable of preventing an excessive amount of oil from being taken into a compression mechanism.
  • a horizontal-type scroll compressor including a housing, an electric motor provided in the housing, and a scroll-type compression mechanism provided in the housing and driven by the electric motor.
  • the housing has a suction port for sucking the working fluid into the housing, and a discharge port for discharging the working fluid compressed by the compression mechanism from the housing.
  • a low pressure chamber communicating with the suction port is formed on one side of the compression mechanism
  • a high pressure chamber communicating with the discharge port is formed on the other side of the compression mechanism
  • the compression mechanism is fixed scroll and fixed scroll
  • the fixed scroll includes an orbiting scroll engaged with the fixed scroll and the fixed scroll includes an end plate, a cylindrical outer peripheral wall erected from the outer peripheral edge of the end plate toward the orbiting scroll, and an outer peripheral wall
  • the spiral scroll includes a spiral wall provided radially inward from the end plate toward the orbiting scroll, and the orbiting scroll includes an end plate and a spiral wall erected from the end plate toward the fixed scroll.
  • the fixed scroll is provided with at least one working fluid inlet for introducing working fluid into the compression mechanism.
  • an oil introducing passage for introducing the oil staying at the lower part of the low pressure chamber into the compression mechanism is provided to penetrate the outer peripheral wall.
  • the position where it has advanced in the direction of revolution of the orbiting scroll, and the winding end of the orbiting scroll is located at the lowest position.
  • An oil discharge path for discharging excess oil from the compression mechanism is provided below the outer winding end below the winding end position when the motor is running.
  • FIG. 1 is an axial sectional view showing the entire outer configuration of a horizontal scroll compressor according to an embodiment of the present invention.
  • 2 is a side view of the rear end surface of the support block shown in FIG. 1 as viewed in the direction of arrow II of FIG. 3 is a side view of the thrust plate shown in FIG. 1 as viewed in the direction of arrow II of FIG.
  • FIG. 4 is a side view of the fixed scroll shown in FIG. 1 as viewed in the axial direction from the side of the orbiting scroll.
  • FIG. 5 is a perspective view of the fixed scroll shown in FIG.
  • FIG. 6A is a view for explaining the revolution of the orbiting scroll with respect to the fixed scroll shown in FIG. 1 and showing the orbiting scroll at the reference position.
  • FIG. 6B is a view for explaining the revolution of the orbiting scroll with respect to the fixed scroll shown in FIG. 1 and showing the orbiting scroll at a position advanced by 90 degrees from the reference position.
  • FIG. 6C is a view for explaining the revolution of the orbiting scroll with respect to the fixed scroll shown in FIG. 1 and showing the orbiting scroll at a position 180 degrees ahead of the reference position.
  • FIG. 6D is a view for explaining the revolution of the orbiting scroll with respect to the fixed scroll shown in FIG. 1 and showing the orbiting scroll at a position advanced by 270 degrees from the reference position.
  • a scroll-type compressor As a scroll-type compressor according to an embodiment of the present invention, a horizontal-type electric scroll-type compressor (hereinafter simply referred to as a "compressor" for simplicity) integrated with a compression mechanism and a motor is shown in the attached drawing.
  • This compressor is suitable for use in a refrigeration cycle using a refrigerant as a working fluid.
  • This compressor is suitably used in the refrigeration cycle of an automotive air conditioner, but is not limited to this application.
  • the compressor 1 has a housing 2. In the housing 2, a scroll type compression mechanism 3 and a motor 4 for driving the compression mechanism 3 are provided.
  • the housing 2 has a suction port 20 for sucking the working fluid (here, refrigerant) into the housing 2 and a discharge port 30 for discharging the working fluid compressed by the compression mechanism 3 from the housing 2. ing.
  • a low pressure chamber 21 communicating with the suction port 20 is formed on one side (right side in FIG. 1) of the compression mechanism 3 and on the other side (left side in FIG. 1) of the compression mechanism 3
  • a high pressure chamber (a chamber including a discharge chamber 23 and a gas-liquid separation chamber 25 described later) in communication with the chamber 30 is formed.
  • the left and right direction in FIG. 1 may be referred to as “axial direction”, the left side in FIG. 1 as “rear side”, and the right side in FIG. 1 as “front side”.
  • a support block 5 is provided at a substantially central portion in the axial direction in the housing 2.
  • the bearing block 5 is provided with a bearing 6.
  • a bearing 7 is also provided on the front wall 2 a of the housing 2.
  • An axially extending drive shaft 8 is rotatably supported via the bearings 6, 7.
  • the rotor 4 a of the motor 4 is fixed to the drive shaft 8, and the stator 4 b of the motor 4 is fixed to the housing 2.
  • the motor 4 is disposed in the low pressure chamber described above.
  • the compression mechanism 3 includes a fixed scroll 10 and a orbiting scroll 11 engaged with the fixed scroll 10 and revolving with respect to the fixed scroll 10.
  • the fixed scroll 10 includes a disk-shaped end plate 10a, a cylindrical outer peripheral wall 10c erected from the outer peripheral edge of the end plate 10a toward the orbiting scroll 11, and the end plate 10a radially inward of the outer peripheral wall 10c.
  • a spiral wall 10 b provided upright toward the orbiting scroll 11.
  • the orbiting scroll 11 has a disk-shaped end plate 11 a and a spiral wall 11 b erected from the end plate 11 a toward the fixed scroll 10.
  • the end plate 11a is formed with a bearing receiver 11e and a plurality of circular recesses 11f.
  • a locking pin 9 pressed into the support block 5 is accommodated in each of the circular recesses 11f.
  • a ring made of a hard material capable of resisting contact with the locking pin 9 is fitted in each circular recess 11 f.
  • the front end portion of the eccentric pin 8a is press-fit into a hole formed at a position shifted from the rotational axis of the drive shaft 8 at the rear end of the drive shaft 8.
  • the rear end portion of the eccentric pin 8 a is inserted into a hole formed in the bush 12.
  • the bush 12 is provided with a balance weight 12 a integrated with the bush 12.
  • the bush 12 is inserted into the inner ring of the bearing 13, and the outer ring of the bearing 13 is attached to the bearing receiver 11 e of the orbiting scroll 11.
  • the orbiting scroll 11 can move relative to the support block 5 within the range of the circle of the circular recess 11 f.
  • the orbiting scroll 11 tries to rotate as the drive shaft 8 rotates, but its movement is restricted by the circular recess 11 f and the anti-rotation pin 9. That is, the circular recess 11 f and the anti-rotation pin 9 prevent the rotation movement while permitting the revolution movement of the orbiting scroll 11.
  • a plurality of (for example, two or three) compression chambers 15 are formed between the scrolls 10 and 11.
  • the compression chambers 15 move to the center side while gradually reducing the internal volume, whereby the working fluid in the compression chambers 15 is compressed.
  • An annular thrust plate 16 made of a highly wear resistant material is held between the front surface of the outer peripheral wall 10 c of the fixed scroll 10 and the front surface of the end plate of the orbiting scroll 11 and the rear surface of the support block 5.
  • the thrust plate 16 has a shape that matches the shape of the end surface of the fixed scroll 10 facing this (see FIG. 2).
  • a central hole 16c sized to allow eccentric rotational movement of the bearing 13 and the balance weight 12a is formed in the central portion of the thrust plate 16.
  • the thrust plate 16 is formed with the same number of holes 16 p as the locking pins 9, and the locking pins 9 pass through the holes 16 p.
  • the thrust plate 16 is positioned relative to the support block 5 by means of the locking pin 9.
  • the working fluid (refrigerant of the refrigeration cycle) introduced into the low pressure chamber from the suction port 20 flows toward the left side of FIG. 1 through the gap where the components of the motor 4 are not provided It is introduced into the compression mechanism 3 from working fluid inlets 10d1, 10d2, 10d3 formed in the outer peripheral wall 10c of the fixed scroll 10.
  • the working fluid is compressed in the compression chamber 15 formed between the fixed scroll 10 and the orbiting scroll 11 as described above, and the housing is from the discharge hole 10 h formed at the center of the end plate 10 a of the fixed scroll 10. It flows into the discharge chamber 23 provided in the inside of 2.
  • the discharge hole 10 h is provided with a check valve 24 in the form of a flap valve, and the check valve 24 opens when the pressure in the compression chamber 15 near the discharge hole 10 h is higher than the pressure in the discharge chamber 23 .
  • a generally cylindrical gas-liquid separation chamber 25 is provided at the rear of the discharge chamber 23.
  • a through hole 26 is formed in a partition between the discharge chamber 23 and the gas-liquid separation chamber 25.
  • a cylindrical guide 27 is provided at a position near the through hole 26 in the gas-liquid separation chamber 25. The working fluid discharged from the through hole 26 flows while rotating around the cylindrical guide 27, and the oil (liquid) contained in the working fluid (gaseous refrigerant) is centrifuged. The working fluid (gaseous refrigerant) from which the oil is separated flows upward through the internal space of the cylindrical guide 27 and is discharged from the housing 2 through the discharge port 30.
  • the centrifuged oil flows down along the inner wall surface of the gas-liquid separation chamber 25 and accumulates in the lower part of the gas-liquid separation chamber 25.
  • An oil storage chamber 28 is formed below the discharge chamber 23.
  • a through hole 29 is formed in a partition between the gas-liquid separation chamber 25 and the oil storage chamber 28.
  • the oil accumulated in the lower part of the gas-liquid separation chamber 25 flows into the oil storage chamber 28 through the through hole 29.
  • the oil in the oil storage chamber 28 passes through the filter 31 and the orifice 32 to fix the fixed scroll 1. It flows into the oil supply passage 33 formed inside 0.
  • continuous oil grooves 51, 52, 53 are formed on the rear end face of the support block 5.
  • the position of the end 51 a of the oil groove 51 coincides with the position of the oil supply passage 33 described above.
  • An opening 16 a is formed in the thrust plate 16 at a position corresponding to the position of the oil supply passage 33.
  • the downstream end of the oil groove 53 opens into a space 5 a in which the bush 12 and the bearings 6, 13 and the like are accommodated.
  • the oil flowing out of the oil storage chamber 28 into the oil supply passage 33 flows into the space 5 a and lubricates the sliding surface between the orbiting scroll 11 and the thrust plate 16, the bearing 13 and the like, and then passes between the bearings 6. Then, it accumulates in the bottom (lower part) of the low pressure chamber 21 (the chamber in which the motor 4 is accommodated) of the housing 2.
  • This oil passes through a groove 2g formed in the bottom wall of the housing 2 and a groove 5g formed in the rear surface of the support block 5 at a position opposite to the groove 2g, and the compression mechanism 3 of the bottom portion of the housing 2 It flows into the oil reservoir 2b in the lower region.
  • the oil in the oil reservoir 2b lubricates and seals the compression mechanism 3.
  • the lower portion (preferably at the lowest position or in the vicinity) of the outer peripheral wall 10c of the fixed scroll 10 flows from the bottom of the low pressure chamber 21 of the housing 2 into the oil reservoir 2b through the grooves 2g and 5g.
  • An oil introduction passage 10 e is formed to introduce the oil accumulated in the accumulation 2 b into the inside of the compression mechanism 3 (that is, between the fixed scroll 10 and the orbiting scroll 11).
  • an oil discharge passage 10 f for discharging excess oil from the compression mechanism 3 is provided on the outer peripheral wall 10 c of the fixed scroll 10 so as to penetrate the outer peripheral wall 10 c.
  • the position at which the oil discharge passage 10f is provided is the advance in the revolving direction (clockwise direction in FIGS. 4 and 5) of the orbiting scroll 11 with respect to the portion at which the oil introduction passage 10e of the outer peripheral wall 10c is provided.
  • the oil introduction path 10e near the lowermost portion of the compression mechanism 3, and in consideration of the arrangement relationship between the working fluid inlets 10d1, 10d2 and 10d3 and the winding end 11d of the orbiting scroll 11, oil discharge
  • the passage 10 f is preferably disposed in the lower half of the compression mechanism 3. Therefore, the advance angle ⁇ is specifically set to, for example, about 20 degrees to 90 degrees (but not limited thereto).
  • the oil discharge passage 10f (in particular, the bottom surface 10g thereof) is inclined to be lower as it goes radially outward of the fixed scroll 10.
  • the advance angle defined as described above represents the positions of the plurality of working fluid inlets 10d1, 10d2 and 10d3 described above. It can also be used for
  • the working fluid inlet 10d1 having the smallest advance angle from the oil introduction path 10e is one of the outer peripheral walls 10c of the fixed scroll 10. , And is provided in the vicinity of the winding end 11d of the orbiting scroll 11 (the winding end 11d of the spiral wall 11b).
  • the oil discharge passage 10 f is provided between the oil introduction passage 10 e and the working fluid inlet 10 d 1 with the smallest advance angle.
  • FIG. 6A shows a state in which the orbiting scroll 11 is at a reference position of 0 (zero) degrees.
  • the orbiting scroll 11 revolves clockwise in the figure as shown in FIGS. 6A to 6D.
  • the orbiting scroll 11 is located at a position advanced by 90 degrees from the reference position in FIG. 6B, at a position advanced by 180 degrees from the reference position in FIG. 6C, and at a position advanced by 270 degrees from the reference position in FIG.
  • the end plate 11a of the orbiting scroll 11 is indicated by a thick solid circle.
  • the height H1 (axial length) (see FIG. 1) of the end plate 11a is substantially equal to the distance H2 from the top of the spiral wall 10b of the fixed scroll 10 to the top of the outer peripheral wall 10c measured in the axial direction. .
  • the surface 10i at the height position (axial position) is expanded.
  • the surface 10i is a flat surface that is entirely perpendicular to the axis, but a groove or a recess may be formed in part of the surface 10i for weight reduction or oil rectification.
  • the area other than the top of the spiral wall 10b and the surface 10i is a spiral recess 10j receiving the spiral wall 11b of the orbiting scroll 11. It has become.
  • the depth of the recess 10 j (the distance from the surface 10 i to the recess 10 j measured in the axial direction) is approximately equal to the height of the spiral wall 11 b.
  • the working fluid When the orbiting scroll 11 is pivoted, the working fluid is drawn from the working fluid inlets 10 d 1, 10 d 2 and 10 d 3 formed in the outer peripheral wall 10 c of the fixed scroll 10 into the space inside the outer peripheral wall 10 c of the fixed scroll 10.
  • the suctioned working fluid is compressed by the two compression chambers 15 formed between the spiral wall 10b of the fixed scroll 10 and the spiral wall 11b of the orbiting scroll 11, and is discharged to the discharge chamber 23 through the discharge hole 10h. Be done.
  • the mechanism of this compression is well known to those skilled in the art and therefore will not be described in detail.
  • FIG. 6A shows that the liquid level (liquid level height) of the oil in the oil reservoir 2b in the lower region of the compression mechanism 3 at the bottom of the housing 2 is the highest liquid level.
  • the oil level may be maximized when, for example, all the oil in the housing 2 has fallen downward immediately after the start of operation. In the steady operation state, since the oil circulates in the refrigeration cycle and in the housing 2, the oil level in the oil reservoir 2b is lower than that shown in FIG. 6A.
  • the oil level is at least higher than the top end of the oil introduction passage 10e, ensuring that the minimum amount of oil required by the compression mechanism 3 penetrates inside the compression mechanism 3
  • the amount of oil is set as In addition, when the oil is at the highest level, the amount of oil is set such that the level of the oil is at a lower level than the bottom of the spiral recess 10j of the fixed scroll 10.
  • the peripheral space is mainly a first space (this is the “suction chamber”) sandwiched by the inner peripheral surface of the outer peripheral wall 10c of the fixed scroll 10 and the outer peripheral surface of the spiral wall 11b of the orbiting scroll 11 in the recess 10j. And the outer peripheral surface of the end plate 11 of the orbiting scroll 11 and the inner peripheral surface of the outer peripheral wall 10c of the fixed scroll 10 in an angle range in which the recess 10j is not formed (an angle range in which the surface 10i is formed). And a second space sandwiched between the two.
  • An oil mist circulating in the peripheral space enters the compression chamber 15 from the suction chamber (the first space), and seals the opposing surfaces of the fixed scroll 10 and the orbiting scroll 11, for example, the opposing surfaces of the spiral wall 10b and the spiral wall 11b. At the same time, it prevents burn-in at the contact portion between both spiral walls.
  • a part of the oil scraped up by the end plate 11 a of the orbiting scroll 11 is discharged from within the peripheral space of the compression mechanism 3 via the oil discharge passage 10 f provided in the fixed scroll 10. (See arrow F2 in FIG. 6B). Therefore, it is possible to prevent the presence of an excessive amount of oil mist in the peripheral space.
  • the oil discharged from the oil discharge passage 10 f flows down along the inner wall surface of the housing 2 and returns to the oil reservoir 2 b.
  • the position is a position at which the peripheral scroll wall 11c proceeds in the direction of revolution of the orbiting scroll 11 with respect to the portion where the oil introduction passage 10e of the outer circumferential wall 10c is provided on the outer peripheral wall 10c of the fixed scroll 10
  • the position of the end 11d when the end 11d of the end of the winding is at the lowermost position (this position substantially coincides with the position of the end of the recess 10j from which the oil is taken into the recess 10j)
  • An oil discharge passage 10f is provided below the outer circumferential wall 10c so as to penetrate the outer circumferential wall 10c.
  • the oil discharge passage 10f By providing the oil discharge passage 10f at this position, the following advantages can be obtained. It becomes easy to discharge the oil scraped up by the end plate 11a of the orbiting scroll 11 when the oil level is high, before it enters the recess 10j. If the oil discharge passage 10f is provided in the range where the suction chamber (the first space) can be formed, the flow of the working fluid sucked into the compression mechanism 3 from the working fluid inlets 10d1, 10d2, 10d3 tends to prevent the oil discharge. It is in. However, by providing the oil discharge passage 10f at the above-mentioned position, such a problem is eliminated or reduced.
  • the oil discharge path 10 f is inclined to become lower as it goes outward in the radial direction of the fixed scroll 10, it is possible to prevent the oil temporarily discharged from the fixed scroll 10 from being returned into the fixed scroll 10. .
  • the oil introduction passage 10 e by providing the oil introduction passage 10 e, a sufficient amount of oil can be introduced into the compression mechanism 3 for sealing and lubrication of the compression mechanism 3.
  • the oil discharge passage 10 f it is possible to prevent an excessive amount of oil from being present in the compression mechanism 3. That is, according to the present embodiment, it is possible to reliably seal and lubricate the compression mechanism 3 and to prevent the efficiency reduction or the oil compression, and an appropriate amount of oil is circulated in the compression mechanism 3. You can do it.

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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)
PCT/JP2018/031857 2017-08-31 2018-08-29 スクロール型圧縮機 WO2019044867A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2019539555A JP7075407B2 (ja) 2017-08-31 2018-08-29 スクロール型圧縮機
CN201880062922.1A CN111133197B (zh) 2017-08-31 2018-08-29 涡旋式压缩机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-167723 2017-08-31
JP2017167723 2017-08-31

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JP (1) JP7075407B2 (zh)
CN (1) CN111133197B (zh)
WO (1) WO2019044867A1 (zh)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021021334A (ja) * 2019-07-24 2021-02-18 トヨタ自動車株式会社 スクロール型流体機械
US20210239116A1 (en) * 2020-02-04 2021-08-05 Hanon Systems Scroll compressor having internal fixed scroll with pillar design
DE102020206692A1 (de) 2020-02-04 2021-08-05 Hanon Systems Spiralverdichter mit innerer fester Spirale mit Säulengestaltung
JP2022029502A (ja) * 2020-08-05 2022-02-18 株式会社石垣 固液分離機
KR20220133800A (ko) * 2021-03-25 2022-10-05 가부시키가이샤 도요다 지도숏키 전동 압축기

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JPH02114787U (zh) * 1989-02-28 1990-09-13
JPH0326889A (ja) * 1989-06-21 1991-02-05 Hitachi Ltd スクロール圧縮機
WO2008096445A1 (ja) * 2007-02-09 2008-08-14 Mitsubishi Heavy Industries, Ltd. スクロール圧縮機および空気調和機
US20170058900A1 (en) * 2015-08-26 2017-03-02 Hyundai Mobis Co., Ltd. Lubrication system of electric compressor

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JP2559603B2 (ja) * 1987-12-14 1996-12-04 三井精機工業株式会社 油冷式横形スクロール圧縮機
JP2000179481A (ja) * 1998-12-14 2000-06-27 Hitachi Ltd スクロール圧縮機
CN1192166C (zh) * 2000-02-22 2005-03-09 Lg电子株式会社 涡旋式压缩机
JP4152678B2 (ja) * 2002-06-13 2008-09-17 松下電器産業株式会社 スクロール圧縮機
JP4003681B2 (ja) * 2003-03-31 2007-11-07 株式会社豊田自動織機 電動圧縮機
JP5880513B2 (ja) * 2013-10-01 2016-03-09 ダイキン工業株式会社 圧縮機

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Publication number Priority date Publication date Assignee Title
JPH02114787U (zh) * 1989-02-28 1990-09-13
JPH0326889A (ja) * 1989-06-21 1991-02-05 Hitachi Ltd スクロール圧縮機
WO2008096445A1 (ja) * 2007-02-09 2008-08-14 Mitsubishi Heavy Industries, Ltd. スクロール圧縮機および空気調和機
US20170058900A1 (en) * 2015-08-26 2017-03-02 Hyundai Mobis Co., Ltd. Lubrication system of electric compressor

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021021334A (ja) * 2019-07-24 2021-02-18 トヨタ自動車株式会社 スクロール型流体機械
US11365733B2 (en) 2020-02-04 2022-06-21 Hanon Systems Scroll compressor having internal fixed scroll with pillar design
DE102020206692A1 (de) 2020-02-04 2021-08-05 Hanon Systems Spiralverdichter mit innerer fester Spirale mit Säulengestaltung
CN113217375A (zh) * 2020-02-04 2021-08-06 翰昂汽车零部件有限公司 具有带有支柱设计的内部固定涡旋件的涡旋压缩机
KR20210099491A (ko) 2020-02-04 2021-08-12 한온시스템 주식회사 필러 디자인을 가지는 내부 고정 스크롤을 가지는 스크롤 압축기
JP2021124114A (ja) * 2020-02-04 2021-08-30 ハンオン システムズ 固定スクロール、及びスクロール圧縮機
KR20220042080A (ko) 2020-02-04 2022-04-04 한온시스템 주식회사 필러 디자인을 가지는 내부 고정 스크롤을 가지는 스크롤 압축기
JP7058301B2 (ja) 2020-02-04 2022-04-21 ハンオン システムズ 固定スクロール、及びスクロール圧縮機
US20210239116A1 (en) * 2020-02-04 2021-08-05 Hanon Systems Scroll compressor having internal fixed scroll with pillar design
KR102482557B1 (ko) * 2020-02-04 2022-12-30 한온시스템 주식회사 필러 디자인을 가지는 내부 고정 스크롤을 가지는 스크롤 압축기
JP2022029502A (ja) * 2020-08-05 2022-02-18 株式会社石垣 固液分離機
JP7406702B2 (ja) 2020-08-05 2023-12-28 株式会社石垣 固液分離機
KR20220133800A (ko) * 2021-03-25 2022-10-05 가부시키가이샤 도요다 지도숏키 전동 압축기
KR102713264B1 (ko) * 2021-03-25 2024-10-02 가부시키가이샤 도요다 지도숏키 전동 압축기

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JP7075407B2 (ja) 2022-05-25
JPWO2019044867A1 (ja) 2020-10-01
CN111133197A (zh) 2020-05-08
CN111133197B (zh) 2022-05-13

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