[go: up one dir, main page]

EP1865201A1 - Spiralfluidmaschine - Google Patents

Spiralfluidmaschine Download PDF

Info

Publication number
EP1865201A1
EP1865201A1 EP06730455A EP06730455A EP1865201A1 EP 1865201 A1 EP1865201 A1 EP 1865201A1 EP 06730455 A EP06730455 A EP 06730455A EP 06730455 A EP06730455 A EP 06730455A EP 1865201 A1 EP1865201 A1 EP 1865201A1
Authority
EP
European Patent Office
Prior art keywords
scroll
rotor
unit
helical groove
refrigerant
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP06730455A
Other languages
English (en)
French (fr)
Other versions
EP1865201A4 (de
EP1865201B1 (de
Inventor
Yoshitaka c/o Sanden Corporation Koitabashi
Kou c/o SANDEN CORPORATION TSUKAMOTO
Tomokazu c/o SANDEN CORPORATION NARUTA
Shigeyuki c/o SANDEN CORPORATION KOYAMA
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanden Corp
Original Assignee
Sanden Corp
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 Sanden Corp filed Critical Sanden Corp
Publication of EP1865201A1 publication Critical patent/EP1865201A1/de
Publication of EP1865201A4 publication Critical patent/EP1865201A4/de
Application granted granted Critical
Publication of EP1865201B1 publication Critical patent/EP1865201B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/045—Heating; Cooling; Heat insulation of the electric motor in 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
    • 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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0085—Prime movers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/803—Electric connectors or cables; Fittings therefor

Definitions

  • the present invention relates to scroll fluid machines, and more particularly, to a scroll fluid machine suited for use as a scroll compressor incorporated in a refrigeration circuit of an automotive air-conditioning system to compress a refrigerant.
  • a scroll compressor of this type is driven by the engine or electric motor of a motor vehicle.
  • the electric motor-driven compressor is easy to adjust the displacement of the refrigerant, irrespective of engine load, and thus is superior in that the temperature in the passenger compartment of the vehicle can be finely controlled.
  • An electric motor-driven scroll compressor disclosed in Unexamined Japanese Patent Publication No. 2003-129983 includes a housing used in common for the scroll unit and the electric motor, and the scroll unit and the armature of the electric motor are contained in the common housing.
  • the compressor disclosed in the above publication includes a cooling passageway for the armature.
  • the cooling passageway guides the refrigerant to the armature before the refrigerant is returned to the scroll unit. Since the temperature of the return refrigerant is considerably lower than the ambient temperature, the armature can be effectively cooled by the return refrigerant.
  • the cooling passageway includes an air gap between the rotor and stator of the armature, a gap between the stator and the inner peripheral wall of the common housing, and gaps between stator coils. These gaps are, however, so narrow that the cooling passageway constitutes a large resistance to the flow of the refrigerant flowing toward the scroll unit, increasing the pressure loss of the refrigerant. Consequently, the scroll unit is unable to efficiently suck in the return refrigerant, so that the suction efficiency of the scroll unit lowers.
  • a motor disclosed in Unexamined Japanese Patent Publication No. 2002-165406 has an armature provided with an axial passage extending through the rotor as well as with fans attached to the respective opposite end faces of the rotor. As the fans rotate, the refrigerant is forced to flow through the axial passage in one direction, thus cooling the armature.
  • the size of the armature increases by an amount corresponding to the axial passage formed through the rotor, which entails increase in the outside diameter and weight of the common housing of the scroll compressor. Further, the use of the fans leads to an increased number of component parts of the armature, increasing the cost of the scroll compressor.
  • An object of the present invention is to provide a scroll fluid machine capable of enhancing the suction efficiency of a scroll unit thereof without entailing increase in size or in the number of component parts.
  • the present invention provides a scroll fluid machine comprising: a housing; a scroll unit contained in the housing, the scroll unit having a fixed scroll and a movable scroll cooperating with each other to compress a working fluid; an armature contained in the housing adjacently to the scroll unit and including a rotor for revolving the movable scroll, the rotor having a peripheral surface and opposite end faces; and a fluid conduit located inside the housing to guide the working fluid toward the scroll unit through the armature and including a helical groove formed in the peripheral surface of the rotor, the helical groove having opposite ends opening in the respective opposite end faces of the rotor.
  • the fluid conduit includes the helical groove formed on the rotor, and thus, a major part of the working fluid supplied to the scroll unit flows through the helical groove.
  • the helical groove increases the cross-sectional area of the fluid conduit, and therefore, the fluid conduit does not constitute a large resistance to the flow of the working fluid flowing toward the scroll unit. As a result, the pressure loss of the working fluid is reduced and the working fluid suction efficiency of the scroll unit improves.
  • the helical groove has a helix direction such that when the rotor is rotated, the working fluid in the helical groove is forced toward the scroll unit.
  • the working fluid in the helical groove is constantly forced toward the scroll unit. Accordingly, the working fluid is forced to flow through the helical groove toward the scroll unit, thus making it possible not only to further reduce the pressure loss of the working fluid but to further enhance the suction efficiency of the scroll unit.
  • the scroll unit is a compression unit for a refrigeration circuit
  • the fluid conduit guides a refrigerant to be returned to the compression unit.
  • the peripheral surface of the rotor having the helical groove formed therein is an outer peripheral surface of the rotor.
  • the temperature of the refrigerant being returned to the compression unit is considerably lower than the ambient temperature, and therefore, when the refrigerant flows through the helical groove of the rotor, the armature is effectively cooled by the refrigerant. Consequently, the armature is prevented from being overheated, whereby the performance of the armature is maintained.
  • the rotor may have a laminated structure obtained by laminating ring-shaped magnetic steel sheets one upon another in an axial direction of the rotor, and each magnetic steel sheet may have a helical groove-forming notch cut in a peripheral edge thereof constituting the peripheral surface of the rotor.
  • the helical groove can be easily formed in the peripheral surface of the rotor.
  • a scroll compressor shown in FIG. 1 is used in an automotive air-conditioning system, that is, in a refrigeration circuit.
  • the compressor has a cylindrical housing 10.
  • the housing 10 has a unit casing 12, a motor casing 14, and a circuit casing 16 arranged in this order as viewed from left to right in FIG. 1.
  • the unit casing 12 and the motor casing 14 are coupled together by a plurality of connecting bolts 18, and the motor casing 14 and the circuit casing 16 are also coupled together by a plurality of connecting bolts 19.
  • the unit casing 12 contains a scroll unit 20 having a fixed scroll 22 and a movable scroll 24.
  • the fixed scroll 22 is abutted against an end wall 12a of the unit casing 12 and fixed to the end wall 12a by fixing bolts 26.
  • the movable scroll 24 is located close to the motor casing 14.
  • the fixed and movable scrolls 22 and 24 have respective spiral walls 22f and 24m engaged with each other.
  • the spiral walls 22f and 24m thus engaged with each other define a plurality of compression chambers 28 therebetween.
  • the compression chambers 28 spirally move in the circumferential direction toward the center of the fixed scroll 22, and in the process of movement, the capacities of the compression chambers 28 decrease by degrees.
  • the unit casing 12 has a discharge chamber 30 defined therein.
  • the discharge chamber 30 has its end walls constituted by the end wall 12a of the unit casing 12 and an end plate 22a of the fixed scroll 22, respectively.
  • the end plate 22a has a discharge hole 32 formed through the center thereof.
  • the discharge hole 32 is opened and closed by a discharge valve (not shown).
  • the discharge valve is arranged inside the discharge chamber 30 and fixed to the end plate 22a of the fixed scroll 22.
  • the unit casing 12 has a discharge port 34 formed in its end wall 12a.
  • the discharge port 34 has an inner end communicating with the discharge chamber 30 and has an outer end connected to a refrigerant circulation path (not shown) of the refrigeration circuit, or more specifically, to a condenser (not shown) of the refrigeration circuit through the refrigerant circulation path.
  • the movable scroll 24 is allowed to revolve but is prevented from rotating on its axis. More specifically, a ball coupling 36 is interposed between an end plate 24a of the movable scroll 24 and one end of the motor casing 14. The ball coupling 36 prevents the movable scroll 24 from rotating on its axis and at the same time transmits the thrust load of the movable scroll 24 to the motor casing 14.
  • the motor casing 14 contains an armature 38.
  • the armature 38 partitions the interior of the motor casing 14 into a chamber 13 close to the unit casing 12 and a chamber 15 close to the circuit casing 16.
  • the armature 38 has a rotary shaft 40 located at the center of the motor casing 14 and extending from the one end of the motor casing 14 to the circuit casing 16.
  • the rotary shaft 40 is rotatably supported at opposite ends by the one end of the motor casing 14 and a partition wall 16a of the circuit casing 16 through a ball bearing 42 and a roller bearing 44, respectively.
  • the partition wall 16a partitions the interior of the circuit casing 16 into a chamber 17 communicating with the interior of the motor casing 14 and a circuit chamber 19 separated from the chamber 17.
  • the rotary shaft 40 has a large-diameter portion 46 formed at one end thereof.
  • the large-diameter end portion 46 has an end face facing the end plate of the movable scroll 24.
  • a crankpin 48 protrudes from the end face of the large-diameter end portion 46 toward the movable scroll 24, and an eccentric bushing 50 is fitted on the crankpin 48.
  • the eccentric bushing 50 is rotatably supported by a boss 24a of the movable scroll 24 through a needle bearing 52.
  • the movable scroll 24 revolves about the fixed scroll 22 while being prevented from rotating on its axis by the ball coupling 36.
  • the revolving radius of the movable scroll 24 is determined by the distance between the axis of the rotary shaft 40 and the axis of the crankpin 48.
  • the armature 38 has a rotor 54 mounted on the rotary shaft 40.
  • the rotor 54 is surrounded by a stator 56 fixed to the inner peripheral wall of the motor casing 14.
  • the circuit casing 16 has a return port 58 formed in its outer peripheral wall.
  • the return port 58 has an inner end communicating with the interior of the motor casing 14, that is, the chamber 15, through the chamber 17 of the circuit casing 16.
  • the other end of the return port 58 is connected to the refrigerant circulation path of the refrigeration circuit, or more specifically, to an evaporator of the refrigeration circuit through the refrigerant circulation path. Accordingly, the return refrigerant delivered from the evaporator flows through the return port 58 into the chamber 17 in the circuit casing 16 and then is supplied from the chamber 17 to the interior of the motor casing 14.
  • a driver circuit 59 for the armature 38 is arranged in the circuit chamber 19 of the circuit casing 16.
  • the driver circuit 59 controls the supply of electric power to the armature 38 and thus the rotation of the armature 38.
  • a cooling conduit is provided in the motor casing 14 and serves to guide the return refrigerant supplied to the motor casing 14 through the armature 38.
  • the cooling conduit includes a helical groove as its principal part, besides an air gap Ga between the rotor 54 and the stator 56, a gap Gb between the inner peripheral wall of the motor casing 14 and the outer peripheral wall of the stator 56, and gaps (not shown) between stator coils. These gaps and the helical groove interconnect the chambers 13 and 15 located on the opposite sides of the armature 38.
  • the rotor 54 has a laminated structure obtained by laminating numerous ring-shaped magnetic steel sheets 62 one upon another in the axial direction of the rotary shaft 40.
  • the helical groove 64 shown in FIG. 2, is formed in the outer peripheral surface of the rotor 54 and has opposite ends opening in the respective opposite end faces of the rotor 54. More specifically, the helical groove 64 has a helix direction similar to that of a right-handed screw such that when the rotor 54 is rotated, the groove makes motion advancing toward the unit casing 12.
  • each magnetic steel sheet 62 has a U-shaped notch 66 cut in an outer peripheral surface thereof.
  • the magnetic steel sheets 62 are laminated one upon the other such that the notches 66 of adjacent magnetic steel sheets are slightly shifted in the circumferential direction of the rotor 54, whereby the helical groove 64 is formed by the notches 66 contiguous with each other in the axial direction of the rotor 54.
  • the helical groove 64 may be formed by mechanically machining the outer peripheral surface of the rotor 54 after the rotor 54 is prepared by laminating a large number of magnetic steel sheets 62.
  • the unit casing 12 has a suction chamber 60 for the scroll unit 20 defined therein.
  • the suction chamber 60 surrounds the movable scroll 24 of the scroll unit 20 and is separated from the aforementioned discharge chamber 30 by the fixed scroll 22.
  • the suction chamber 60 is connected with the chamber 13 in the motor casing 14 through the internal space of the ball coupling 36, the space between the movable scroll 24 and the ball bearing 42, and the internal space of the ball bearing 42. Accordingly, the suction chamber 60 is connected with the return port 58 of the circuit casing 16 through a refrigerant conduit including the aforementioned cooling conduit, whereby the return refrigerant flowing into the return port 58 is supplied to the suction chamber 60 through the refrigerant conduit.
  • the compression chamber 28 thereafter moves toward the discharge hole 32 of the fixed scroll 22 as the movable scroll 24 further revolves, and since the capacity of the compression chamber 28 decreases in the process of revolution, the refrigerant sucked in the compression chamber 28 is compressed.
  • the compression chamber 28 then reaches the discharge hole 32, and when the refrigerant pressure in the compression chamber 28 surpasses the valve closing pressure of the discharge valve, the discharge valve opens, whereupon the compressed refrigerant in the compression chamber 28 is discharged to the discharge chamber 30 through the discharge hole 32.
  • the compressed refrigerant in the discharge chamber 30 is delivered through the discharge port 34 to the refrigerant circulation path and supplied to the condenser of the refrigeration circuit. Subsequently, the compressed refrigerant is supplied via a receiver and an expansion valve in the refrigerant circulation path to the evaporator, which returns the refrigerant to the return port 58.
  • the refrigerant thus returned to the return port 58 flows into the chamber 17 in the circuit casing 16 and then is supplied to the suction chamber 60 through the aforementioned refrigerant conduit, namely, the cooling conduit.
  • the temperature of the return refrigerant is considerably lower than the ambient temperature, as stated above, and therefore, the return refrigerant effectively cools the armature 38 while passing through the cooling conduit, thus preventing the armature 38 from becoming overheated.
  • the cooling conduit includes the helical groove 64 as its principal part and the helical groove 64 serves to increase the effective cross-sectional flow area of the cooling conduit as a whole. Consequently, the cooling conduit does not constitute a large resistance to the flow of the return refrigerant flowing toward the suction chamber 60, so that the pressure loss of the return refrigerant is small.
  • the return refrigerant in the helical groove 64 is forced to move toward the unit casing 12, thus producing a flow of the return refrigerant in the helical groove 64 directed from the chamber 15 to the chamber 13 of the motor casing 14.
  • the helical groove 64 does not entail increase in the diameter of the rotor 54 or in the number of component parts of the armature 38, so that the scroll compressor need not be increased in size. Furthermore, the weight of the scroll compressor can be reduced.
  • the rotor 54 may have a plurality of helical grooves 64 formed in the outer peripheral surface thereof. Also, one or more helical grooves 64 may be formed in the inner peripheral surface of the rotor, instead of the outer peripheral surface of same.
  • the present invention is equally applicable to a scroll expander, besides the compressor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP06730455A 2005-04-01 2006-03-29 Spiralfluidmaschine Not-in-force EP1865201B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005106098A JP2006283694A (ja) 2005-04-01 2005-04-01 スクロール型流体機械
PCT/JP2006/306507 WO2006106753A1 (ja) 2005-04-01 2006-03-29 スクロール型流体機械

Publications (3)

Publication Number Publication Date
EP1865201A1 true EP1865201A1 (de) 2007-12-12
EP1865201A4 EP1865201A4 (de) 2008-07-23
EP1865201B1 EP1865201B1 (de) 2010-11-10

Family

ID=37073316

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06730455A Not-in-force EP1865201B1 (de) 2005-04-01 2006-03-29 Spiralfluidmaschine

Country Status (6)

Country Link
US (1) US20090148314A1 (de)
EP (1) EP1865201B1 (de)
JP (1) JP2006283694A (de)
CN (1) CN101151465A (de)
DE (1) DE602006018117D1 (de)
WO (1) WO2006106753A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2733357A1 (de) * 2012-11-15 2014-05-21 Kabushiki Kaisha Toyota Jidoshokki Motorbetriebener Verdichter
EP2159425A3 (de) * 2008-09-02 2014-08-27 Kabushiki Kaisha Toyota Jidoshokki Motorbetriebener Verdichter

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5018450B2 (ja) * 2007-12-18 2012-09-05 株式会社豊田自動織機 電動圧縮機
JP5109642B2 (ja) * 2007-12-18 2012-12-26 株式会社豊田自動織機 電動圧縮機
CN101619721B (zh) * 2009-07-24 2010-11-17 南京银茂压缩机有限公司 汽车空调用一体式电动涡旋压缩机总成
KR101682250B1 (ko) * 2010-12-06 2016-12-02 한온시스템 주식회사 전동식 압축기
KR101358602B1 (ko) 2011-08-31 2014-02-04 한라비스테온공조 주식회사 전동 압축기
JP5867313B2 (ja) * 2012-06-28 2016-02-24 株式会社豊田自動織機 電動圧縮機
JP6842385B2 (ja) * 2017-08-25 2021-03-17 三菱重工サーマルシステムズ株式会社 スクロール圧縮機

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0306405A1 (de) * 1987-09-04 1989-03-08 Bernard Zimmern Verfahren und Vorrichtung für Kühlung des Motors einer Kühlmaschine durch flüssiges und gasförmiges Medium des Ekonomisers
JPH05302581A (ja) * 1992-04-24 1993-11-16 Daikin Ind Ltd 縦形圧縮機
JP2004204791A (ja) * 2002-12-26 2004-07-22 Fujitsu General Ltd 密閉型圧縮機

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2568915B2 (ja) * 1989-07-19 1997-01-08 イビデン株式会社 Ｉｃカード
JPH0351196U (de) * 1989-09-26 1991-05-17
JPH0932729A (ja) * 1995-07-19 1997-02-04 Mitsubishi Heavy Ind Ltd 電動圧縮機
JP3870642B2 (ja) * 1999-12-21 2007-01-24 株式会社デンソー 電動圧縮機
JP3475174B2 (ja) * 2000-02-10 2003-12-08 東芝テック株式会社 電動ポンプ
JP4356232B2 (ja) 2000-11-22 2009-11-04 株式会社デンソー ロータ重心偏心型モータ
JP4372511B2 (ja) * 2003-10-17 2009-11-25 トヨタ自動車株式会社 軸受間に延在する筒部材を有する回転電機付き過給機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0306405A1 (de) * 1987-09-04 1989-03-08 Bernard Zimmern Verfahren und Vorrichtung für Kühlung des Motors einer Kühlmaschine durch flüssiges und gasförmiges Medium des Ekonomisers
JPH05302581A (ja) * 1992-04-24 1993-11-16 Daikin Ind Ltd 縦形圧縮機
JP2004204791A (ja) * 2002-12-26 2004-07-22 Fujitsu General Ltd 密閉型圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2006106753A1 *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2159425A3 (de) * 2008-09-02 2014-08-27 Kabushiki Kaisha Toyota Jidoshokki Motorbetriebener Verdichter
EP2733357A1 (de) * 2012-11-15 2014-05-21 Kabushiki Kaisha Toyota Jidoshokki Motorbetriebener Verdichter
US9243638B2 (en) 2012-11-15 2016-01-26 Kabushiki Kaisha Toyota Jidoshokki Motor-driven compressor including a rotor core having a refrigerant passage

Also Published As

Publication number Publication date
CN101151465A (zh) 2008-03-26
EP1865201A4 (de) 2008-07-23
US20090148314A1 (en) 2009-06-11
JP2006283694A (ja) 2006-10-19
WO2006106753A1 (ja) 2006-10-12
DE602006018117D1 (de) 2010-12-23
EP1865201B1 (de) 2010-11-10

Similar Documents

Publication Publication Date Title
EP1865201B1 (de) Spiralfluidmaschine
US6234769B1 (en) Hybrid type compressor driven by engine and electric motor
US20190203709A1 (en) Motor-operated compressor
EP2072821A2 (de) Motorbetriebener Verdichter
US8858192B2 (en) Screw compressor
JP5527349B2 (ja) ベーン型圧縮機
US11015598B2 (en) Compressor having bushing
MXPA01001177A (es) Compresor de espiral.
JPH0861269A (ja) スクロール型圧縮機
EP3947975B1 (de) Verdichter mit gerichteter absaugung
US20230015175A1 (en) Screw compressor, and refrigeration device
EP3078859B1 (de) Rotationsverdichter und verdichtereinheit dafür sowie klimaanlage
US11136982B2 (en) Screw compressor
CN113167273B (zh) 根据螺旋原理的容积式机器，特别是用于车辆空调机组的涡旋式压缩机
JP2017186924A (ja) 圧縮機
US11566624B2 (en) Compressor having lubrication system
US6589026B2 (en) Fluid machinery having a helical mechanism with through holes for ventilation
JP2012013029A (ja) 圧縮機
JP2005344658A (ja) 電動気体圧縮機
KR20210130861A (ko) 압축기 및 이를 포함하는 공조시스템
JP7546419B2 (ja) スクロール圧縮機
US12092111B2 (en) Compressor with oil pump
KR102443952B1 (ko) 전동 압축기
JP3456878B2 (ja) ヘリカルコンプレッサ
EP2554845A1 (de) Elektrisch betriebener gaskompressor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20070905

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20080619

RBV Designated contracting states (corrected)

Designated state(s): DE FR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIN1 Information on inventor provided before grant (corrected)

Inventor name: KOITABASHI, YOSHITAKA,C/O SANDEN CORPORATION

Inventor name: KOYAMA, SHIGEYUKI,C/O SANDEN CORPORATION

Inventor name: TSUKAMOTO, KOU,C/O SANDEN CORPORATION

Inventor name: NARUTA, TOMOKAZU,C/O SANDEN CORPORATION

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR

REF Corresponds to:

Ref document number: 602006018117

Country of ref document: DE

Date of ref document: 20101223

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20110811

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602006018117

Country of ref document: DE

Effective date: 20110811

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 602006018117

Country of ref document: DE

Representative=s name: PRUEFER & PARTNER MBB PATENTANWAELTE RECHTSANW, DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 602006018117

Country of ref document: DE

Owner name: SANDEN HOLDINGS CORPORATION, LSESAKI-SHI, JP

Free format text: FORMER OWNER: SANDEN CORP., ISESAKI, GUNMA, JP

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20160321

Year of fee payment: 11

REG Reference to a national code

Ref country code: FR

Ref legal event code: CD

Owner name: SANDEN HOLDINGS CORPORATION, JP

Effective date: 20160525

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20160330

Year of fee payment: 11

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602006018117

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20171130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171003

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170331