WO2004111456A1 - スクロール圧縮機 - Google Patents
スクロール圧縮機 Download PDFInfo
- Publication number
- WO2004111456A1 WO2004111456A1 PCT/JP2004/008373 JP2004008373W WO2004111456A1 WO 2004111456 A1 WO2004111456 A1 WO 2004111456A1 JP 2004008373 W JP2004008373 W JP 2004008373W WO 2004111456 A1 WO2004111456 A1 WO 2004111456A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- scroll compressor
- lubricating oil
- outer region
- spiral part
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/005—Axial sealings for working fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/023—Lubricant distribution through a hollow driving shaft
Definitions
- the present invention relates to a scroll compressor used in refrigeration cycle apparatus such as, in particular, R 4 1 OA boiled carbon dioxide (C 0 2) scroll compressor which is suitable for vapor compression refrigeration cycle using a refrigerant such as.
- a scroll compressor used in refrigeration cycle apparatus such as, in particular, R 4 1 OA boiled carbon dioxide (C 0 2) scroll compressor which is suitable for vapor compression refrigeration cycle using a refrigerant such as.
- FIG. 5 shows an example of a conventional configuration described in Patent Document 1 (Japanese Patent Application Laid-Open No. 2-280252). That is, in the conventional scroll compressor, the back pressure chamber 12 is provided on the surface of the orbiting spiral part 5 on the side opposite (back side) to the orbiting spiral blade surface, and the back pressure chamber 12 is formed in the inner area by the annular seal 11.
- the refrigerant is a high-pressure refrigerant such as carbon dioxide (co 2 )
- the absolute value of the thrust force pressing the swirling spiral part 5 against the fixed spiral part 4 increases, and the set back pressure ⁇ ⁇ Since the absolute value of (2 P m—P s) also increases, the delay in refueling is longer than in the case of refrigerant R 410 A, so that the fixed spiral part 4 and swirl spiral part 5 There has been a problem that sticking is more likely to occur.
- an object of the present invention is to provide a highly reliable scroll compressor that prevents a delay in refueling at the time of startup. Disclosure of the invention
- the scroll compressor according to the first embodiment of the present invention includes a plurality of compression units that combine a fixed spiral component having fixed spiral blades on a fixed head plate and a revolving spiral component having revolving spiral blades on a revolving head plate.
- a space is formed, and a back pressure chamber is provided on the surface opposite to the swirling blade surface of the swirling spiral part.
- the back pressure chamber is divided into an inner area and an outer area by an annular seal, and discharge pressure is applied to the inner area of the annular seal.
- the lubricating oil in a state is supplied, a part of the lubricating oil is decompressed by the throttle portion and supplied to the outer region, and the lubricating oil in the outer region is supplied to the suction space.
- the swirling spiral part can be brought into contact with the fixed spiral part by only the discharge pressure Pd acting on the inner area of the annular seal.
- the pressure Pm acting on the outer region of the annular seal can be set to a suction pressure Ps or a pressure close to Ps.
- the ratio ( ⁇ ⁇ / ⁇ o) is set to be substantially constant and 0.2 or less.
- the pressure Pm in the outer region of the annular seal rises due to the inflow of the lubricating oil from the inner region of the annular seal, but the set pressure Pm is lower (i.e., the suction pressure Pm). s or a pressure close to P s), the saturation vapor pressure P at 0 ° C of the refrigerant used to reach that value in a short time.
- the saturation vapor pressure P at 0 ° C of the refrigerant used to reach that value in a short time.
- a scroll compressor according to the first or second embodiment, wherein the refrigerant gas sucked into the suction space includes a liquid cooling medium having a dryness of 0.5 or less. It is a gas.
- the present embodiment when the refrigerant gas containing the liquid refrigerant is sucked in at the time of startup, and when the dryness of the refrigerant gas is 0.5 or less, lubricating oil can be supplied quickly at the time of startup. As a result, the reliability of the scroll compressor can be ensured.
- the fourth embodiment of the present invention is the scroll compressor according to the first or second embodiment, wherein carbon dioxide is used as a refrigerant.
- FIG. 1 is a longitudinal sectional view showing a scroll compressor according to a first embodiment of the present invention.
- Fig. 2 is a partial perspective view showing the orbiting spiral parts and the annular seal of the scroll compressor shown in Fig. 1.
- Fig. 3 is a diagram showing the relationship between the diameter ratio (dZD) of the scroll compressor shown in Fig. 1 and the thrust force.
- FIG. 4 is a diagram showing a time and a pressure change after the start of the scroll compressor according to the second embodiment of the present invention.
- FIG. 5 is a longitudinal sectional view showing a conventional scroll compressor.
- FIG. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention, and a compression target is a refrigerant gas.
- the scroll compressor includes a main bearing member 7 of a crankshaft 6 fixed in a closed container 1 by welding or shrink fitting, and a bolt mounted on the main bearing member.
- a scroll type compression mechanism 2 is configured by sandwiching a revolving spiral part 5 that interlocks with the fixed spiral part 4 between the fixed spiral part 4 that has been stopped.
- a rotation restraining part 1 mm such as an Oldham ring is provided between the swirling spiral part 5 and the main bearing member to prevent rotation of the swirling spiral part 5 and guide the swirling spiral part 5 to move in a circular orbit.
- the orbiting spiral part 5 is eccentrically driven by the eccentric part at the upper end to make the orbiting spiral part 5 make a circular orbital motion.
- the compression formed by combining the fixed spiral blade 4b provided on the fixed end plate 4a of the fixed spiral component 4 and the swirling spiral blade 5b provided on the swivel end plate 5a of the spiral component 5 Take advantage of the fact that space 8 becomes smaller while moving from the outer Then, the refrigerant gas is sucked from the suction vessel 1 and the suction space 9 on the outer periphery of the fixed spiral part 4 and compressed, and the medium gas that has reached a predetermined pressure or higher is discharged from the suction pipe 18 and the fixed spiral part 4 to the fixed spiral part 4. This is a configuration in which discharge from the central discharge port into the closed container 1 is repeated.
- the lower end of the crankshaft 6 reaches the lubricating oil reservoir 1 at the lower end of the closed casing 1 and is supported by the auxiliary bearing member 15 to rotate stably.
- the sub-bearing member 15 is attached to a sub-bearing holding member 14 that is welded or shrink-fitted and fixed in the sealed container 1.
- the electric motor 3 is located between the main bearing member R and the sub bearing member 14, and is integrally fixed around the outer periphery of the crankshaft 6 with the stator 3 a fixed to the closed casing 1 by welding or shrink fitting.
- the rotating spiral part 5 makes a circular orbital movement when the rotor 3a and the crankshaft 6 rotate.
- a back pressure chamber 12 is provided at the back of the swirling spiral part 5.
- an annular seal 11 is arranged in an annular groove provided in the main bearing member, and the annular seal 11 divides the back pressure chamber 12 into two parts.
- a high discharge pressure Pd is applied to one inner region 12 a divided by the annular seal 11.
- a predetermined intermediate pressure Pm between the suction pressure Ps and the discharge pressure Pd is applied to the outer region 12b.
- the swirling spiral part 5 has a configuration in which a thrust force is applied by the pressure of the back pressure chambers 12 and is stably pressed against the fixed spiral part 4 to reduce leakage and, at the same time, stably operate in a circular orbit. is there.
- a positive displacement oil pump 16 is attached to the auxiliary bearing holding member 14.
- the oil pump 16 is driven at the lower end of the crankshaft 6.
- the lubricating oil sucked up from the lubricating oil reservoir 1 by the oil pump 16 is supplied to each sliding portion of the compression mechanism 2 through a lubricating oil supply hole 6 a penetrating through the crankshaft 6.
- Most of the lubricating oil supplied to the upper end of the crankshaft 6 through the lubricating oil supply 6 6a flows under the main bearing member 7 after lubricating the eccentric bearing portion and the main bearing portion a of the crankshaft 6 Finally, return to the lubricating oil pool.
- a part of the lubricating oil supplied to the upper end of the crankshaft 6 passes through a passage provided inside the swirling spiral part 5 and a throttle part 13, and is decompressed there, thereby forming a region outside the annular seal 11. Supplied to 1 2b.
- a rotation restraining part 1 mm is disposed in the outer region 12 b, and the supplied fluid is provided. Lubrication is provided by lubricating oil. As the lubricating oil supplied to the outer region 1 2b accumulates, the pressure in the outer region 1 2b increases, but in order to keep the pressure constant, the outer region 1 2b of the annular seal 1 1 A pressure adjusting mechanism 20 is arranged between the suction spaces 9.
- the pressure adjusting mechanism 20 When the pressure of the outer region 1 2 b becomes higher than the set back pressure ⁇ (2 P m— P s), the pressure adjusting mechanism 20 is activated, and the lubricating oil in the outer region 12 b is drawn into the suction space. 9 and the pressure in the outer region 1 2b is kept almost constant.
- the lubricating oil supplied to the suction space 9 enters the compression space 8 and plays a role of a seal for preventing refrigerant gas from leaking in the compression space 8 and a role of lubricating the sliding surfaces of the fixed spiral part 4 and the swirl spiral part 5.
- the configuration of the scroll compressor according to the first embodiment is as follows.
- the relationship of the ratio (d ZD) between the diameter D of the revolving end plate 5 a of the revolving spiral part 5 and the outer diameter d of the annular seal 11 shown in FIG. Set to a value larger than 5.
- the annular seal 11 is disposed on the side of the swirling spiral part 5 opposite to the surface of the swirling spiral blade 5b, that is, on the back pressure chamber 12 side.
- the pressure ratio PdZPs of the discharge pressure Pd and the suction pressure Ps varies in the range of about 2 to 6 depending on the operating conditions.
- Fig. 3 shows the operation in the case where Pd acts on the inner area 12a of the annular seal 11 in the back pressure chamber 12 of the swirling spiral part 5, and Ps acts on the outer area 12b.
- the thrust force was calculated from the pressure balance acting on the swivel head 5a of the swirling spiral part 5 by changing the conditions, and the relationship between the thrust force and the diameter ratio d ZD is shown.
- the thrust force is always changed when the pressure ratio PdZPs changes in the range of about 2 to 6 in order to slide the swirling spiral part 5 into contact with the fixed spiral part 4. Since it is sufficient if it is plus (+), it can be seen that the outer diameter of the annular seal 11 should be set to be larger than about 0.5 times the diameter of the revolving end plate 5a of the revolving spiral part 5.
- the diameter ratio d ZD is set to be larger than 0.5, a positive (+) thrust force is always obtained regardless of the magnitude of the discharge pressure, so that it acts on the inner region 12 a of the annular seal 11.
- the intermediate pressure Pm acting on the outer region 12b of the annular seal 11 can be set to a suction pressure Ps or a pressure close to Ps.
- the pressure adjusting mechanism 20 is set so as to operate even when the back pressure ⁇ is close to about zero.
- the lubricating oil supplied to the outer region 12 b of the annular seal 11 is supplied to the suction space 9 without time delay. Become. Therefore, even if a large amount of refrigerant liquid is sucked into the suction space 9 at the beginning of startup and the refrigerant liquid flushes the lubricating oil, new lubricating oil is immediately supplied to the suction space 9 and seizure occurs on the sliding surface. A great effect that the phenomenon does not occur can be obtained.
- the pressure in the outer region 1 2b of the annular seal 11 rises due to the flow of lubricating oil from the inner region 12a of the annular seal 11, but reaches the value in a shorter time as the set back pressure is lower .
- the lubricating oil is supplied to the suction space 9 of the compression mechanism 2. Therefore, in the present embodiment, the back pressure ⁇ and the saturated vapor pressure P of the refrigerant used at 0 ° C.
- the value of the back pressure ⁇ ⁇ is defined by the pressure adjusting mechanism 20 embedded in the fixed spiral part 4 so that the ratio ( ⁇ ⁇ ⁇ ⁇ ) to the pressure is approximately constant and not more than 0.2. I have.
- the lubricating oil is supplied to the suction space 9 immediately at startup. Will be done. That is, when the delay in supplying the lubricating oil to the suction space 9 is reduced, an effect is obtained in which the refrigerant liquid is sucked into the suction space from the initial stage of the start and the seizure phenomenon on the sliding surface does not occur.
- the back pressure reaches ⁇ . 5MPa after about 3 ⁇ seconds from the start of operation, and 1. 45MPa after about 45 seconds and 1.5MPa. It took about 60 seconds to reach a.
- the back pressure ⁇ is set to 0.5MPa
- lubricating oil is supplied to the suction space 9 about 3 ⁇ seconds after the start of operation, but the back pressure ⁇ P is set to 1.
- the lubricating oil will not be supplied to the suction space 9 until approximately 45 seconds have elapsed since the start of operation.
- the size of the outer diameter d of the annular seal 11 is set to ⁇ .5 or more of the turning head 5a of the turning spiral part 5a and the diameter D. It is desirable to do that.
- the back pressure ⁇ is set to be small, even if a large amount of refrigerant liquid (that is, a refrigerant having a dryness of 0.5 or less) is sucked into the suction space 9, the swirling spiral portion It has been confirmed that no seizure occurred on the sliding surfaces of the product 5 and the fixed spiral component 4.
- the ratio (d ZD) of the diameter D of the rotating end plate of the swirling spiral part to the outer diameter d of the annular seal is set to be larger than 0.5.
- the pressure Pm acting on the outer area of the ring seal may be set to a pressure close to the suction pressure Ps or Ps.
- the back pressure ⁇ is set to a small value so that the ratio ( ⁇ ⁇ ⁇ ⁇ ) is approximately constant and not more than 0.2, so that the pressure in the outer region of the annular seal is short.
- the set value is reached, and the lubricating oil is promptly supplied to the suction space of the compressor mechanism, that is, the supply delay of the lubricating oil to the suction space is reduced.
- an effect is obtained in which the refrigerant having a dryness of 0.5 or less is sucked into the suction space from the initial stage of the startup and the seizure phenomenon on the sliding surface does not occur.
- the refrigerant sucked into the suction space is a refrigerant gas containing a liquid refrigerant having a dryness of 0.5 or less
- the reliability of the scroll compressor can be improved.
- C 0 2 to the refrigerant since a high absolute value of the pressure of C_ ⁇ 2 itself, but generally tends to occur sticking phenomenon in correspondingly sliding surface of the annular seal in the outer regions
- the back pressure ⁇ ⁇ ⁇ ⁇ By setting the back pressure ⁇ ⁇ ⁇ ⁇ to a small value, at startup, the back pressure rises to the set value in a short time, and the lubricating oil is quickly supplied to the suction space. The phenomenon can be prevented.
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/560,037 US7614859B2 (en) | 2003-06-12 | 2004-06-09 | Scroll compressor with certain pressure ratio between discharge pressure and suction pressure and with certain ratio of diameter of orbiting mirror plate and outer diameter of the annular seal |
KR1020057023664A KR101082710B1 (ko) | 2003-06-12 | 2004-06-09 | 스크롤 압축기 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003-168215 | 2003-06-12 | ||
JP2003168215A JP4440564B2 (ja) | 2003-06-12 | 2003-06-12 | スクロール圧縮機 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004111456A1 true WO2004111456A1 (ja) | 2004-12-23 |
Family
ID=33549328
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/008373 WO2004111456A1 (ja) | 2003-06-12 | 2004-06-09 | スクロール圧縮機 |
Country Status (5)
Country | Link |
---|---|
US (1) | US7614859B2 (ja) |
JP (1) | JP4440564B2 (ja) |
KR (1) | KR101082710B1 (ja) |
CN (2) | CN1823227A (ja) |
WO (1) | WO2004111456A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
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DE112006001283B4 (de) * | 2005-05-23 | 2014-12-11 | Danfoss Commercial Compressors | Kältemittelverdichter vom Scroll-Typ |
US11703052B2 (en) * | 2018-12-06 | 2023-07-18 | Samsung Electronics Co., Ltd. | High pressure scroll compressor |
Families Citing this family (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1830067B1 (en) * | 2004-12-22 | 2017-01-25 | Mitsubishi Denki Kabushiki Kaisha | Scroll compressor |
JP2007138828A (ja) | 2005-11-18 | 2007-06-07 | Hitachi Appliances Inc | スクロール流体機械、冷凍サイクル装置 |
JP2008232041A (ja) * | 2007-03-22 | 2008-10-02 | Mitsubishi Heavy Ind Ltd | 多段圧縮機 |
JP5315933B2 (ja) * | 2008-06-05 | 2013-10-16 | 株式会社豊田自動織機 | 電動スクロール型圧縮機 |
KR101484538B1 (ko) * | 2008-10-15 | 2015-01-20 | 엘지전자 주식회사 | 스크롤 압축기 및 이를 적용한 냉동기기 |
JP2012017656A (ja) * | 2010-07-06 | 2012-01-26 | Sanden Corp | スクロール型圧縮機 |
CN103052804B (zh) * | 2011-03-18 | 2016-01-20 | 松下电器产业株式会社 | 压缩机 |
CN102812251B (zh) * | 2011-03-18 | 2015-06-10 | 松下电器产业株式会社 | 压缩机 |
DE102012104045A1 (de) * | 2012-05-09 | 2013-11-14 | Halla Visteon Climate Control Corporation 95 | Kältemittelscrollverdichter für Kraftfahrzeugklimaanlagen |
JP6108275B2 (ja) * | 2012-05-14 | 2017-04-05 | パナソニックIpマネジメント株式会社 | 圧縮機 |
JP5933042B2 (ja) * | 2013-01-16 | 2016-06-08 | 三菱電機株式会社 | 密閉形圧縮機及びこの密閉形圧縮機を備えた蒸気圧縮式冷凍サイクル装置 |
CN104295498B (zh) | 2013-06-27 | 2017-04-12 | 艾默生环境优化技术有限公司 | 压缩机 |
US20170089624A1 (en) * | 2014-03-19 | 2017-03-30 | Mitsubishi Electric Corporation | Hermetic compressor and vapor compression-type refrigeration cycle device including the hermetic compressor |
CN104088786B (zh) * | 2014-06-24 | 2016-09-07 | 广东广顺新能源动力科技有限公司 | 一种汽车涡旋式电动空调压缩机总成 |
US10641269B2 (en) | 2015-04-30 | 2020-05-05 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Lubrication of scroll compressor |
CN105201837B (zh) * | 2015-10-26 | 2017-11-17 | 珠海格力节能环保制冷技术研究中心有限公司 | 一种双级压缩机及其中间增焓压力的调节方法和控制系统 |
JP2017089427A (ja) * | 2015-11-05 | 2017-05-25 | 三菱重工業株式会社 | スクロール圧縮機、スクロール圧縮機の製造方法 |
DE102015120151A1 (de) * | 2015-11-20 | 2017-05-24 | OET GmbH | Verdrängermaschine nach dem Spiralprinzip, Verfahren zum Betreiben einer Verdrängermaschine, Fahrzeugklimaanlage und Fahrzeug |
JP6738170B2 (ja) * | 2016-03-15 | 2020-08-12 | サンデン・オートモーティブコンポーネント株式会社 | スクロール圧縮機 |
US10414241B2 (en) | 2016-06-30 | 2019-09-17 | Emerson Climate Technologies, Inc. | Systems and methods for capacity modulation through eutectic plates |
US10569620B2 (en) | 2016-06-30 | 2020-02-25 | Emerson Climate Technologies, Inc. | Startup control systems and methods to reduce flooded startup conditions |
CN106286294B (zh) * | 2016-09-19 | 2019-06-07 | 珠海格力电器股份有限公司 | 涡旋压缩机 |
DE102017110913B3 (de) | 2017-05-19 | 2018-08-23 | OET GmbH | Verdrängermaschine nach dem Spiralprinzip, Verfahren zum Betreiben einer Verdrängermaschine, Fahrzeugklimaanlage und Fahrzeug |
KR20200095994A (ko) * | 2019-02-01 | 2020-08-11 | 엘지전자 주식회사 | 결합 구조가 개선된 스크롤 압축기 |
JP6927279B2 (ja) * | 2019-12-17 | 2021-08-25 | ダイキン工業株式会社 | 圧縮機 |
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JP2631839B2 (ja) * | 1986-08-22 | 1997-07-16 | 株式会社日立製作所 | スクロール圧縮機 |
JPH06264876A (ja) * | 1993-03-15 | 1994-09-20 | Toshiba Corp | スクロ−ル形圧縮機 |
JP2000136782A (ja) * | 1998-10-30 | 2000-05-16 | Denso Corp | スクロール型圧縮機 |
JP2000220585A (ja) * | 1999-01-28 | 2000-08-08 | Toyota Autom Loom Works Ltd | スクロール型圧縮機 |
JP3961189B2 (ja) | 2000-03-31 | 2007-08-22 | 松下電器産業株式会社 | 密閉型圧縮機とその気液分離吐出方法 |
-
2003
- 2003-06-12 JP JP2003168215A patent/JP4440564B2/ja not_active Expired - Fee Related
-
2004
- 2004-06-09 US US10/560,037 patent/US7614859B2/en not_active Expired - Fee Related
- 2004-06-09 KR KR1020057023664A patent/KR101082710B1/ko active IP Right Grant
- 2004-06-09 CN CNA2004800200568A patent/CN1823227A/zh active Pending
- 2004-06-09 WO PCT/JP2004/008373 patent/WO2004111456A1/ja active Application Filing
- 2004-06-09 CN CN201010196249A patent/CN101846074A/zh active Pending
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JPS60128992A (ja) * | 1983-12-14 | 1985-07-10 | Hitachi Ltd | スクロ−ル圧縮機 |
JPH07119652A (ja) * | 1993-10-20 | 1995-05-09 | Fujitsu General Ltd | スクロール圧縮機 |
JP2000283066A (ja) * | 1999-03-30 | 2000-10-10 | Sanyo Electric Co Ltd | スクロール圧縮機 |
WO2002063171A1 (fr) * | 2001-02-07 | 2002-08-15 | Mitsubishi Denki Kabushiki Kaisha | Compresseur a conduit spirale |
JP2003035286A (ja) * | 2001-05-18 | 2003-02-07 | Matsushita Electric Ind Co Ltd | スクロール圧縮機とその駆動方法 |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112006001283B4 (de) * | 2005-05-23 | 2014-12-11 | Danfoss Commercial Compressors | Kältemittelverdichter vom Scroll-Typ |
US11703052B2 (en) * | 2018-12-06 | 2023-07-18 | Samsung Electronics Co., Ltd. | High pressure scroll compressor |
Also Published As
Publication number | Publication date |
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US20080038133A1 (en) | 2008-02-14 |
JP4440564B2 (ja) | 2010-03-24 |
KR101082710B1 (ko) | 2011-11-15 |
CN1823227A (zh) | 2006-08-23 |
US7614859B2 (en) | 2009-11-10 |
JP2005002922A (ja) | 2005-01-06 |
KR20060020665A (ko) | 2006-03-06 |
CN101846074A (zh) | 2010-09-29 |
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