EP1770281A2 - Compresseur pour fluide réfrigérant - Google Patents

Compresseur pour fluide réfrigérant Download PDF

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Publication number
EP1770281A2
EP1770281A2 EP06019416A EP06019416A EP1770281A2 EP 1770281 A2 EP1770281 A2 EP 1770281A2 EP 06019416 A EP06019416 A EP 06019416A EP 06019416 A EP06019416 A EP 06019416A EP 1770281 A2 EP1770281 A2 EP 1770281A2
Authority
EP
European Patent Office
Prior art keywords
lubricant
compressor according
space
compressor
outer housing
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
EP06019416A
Other languages
German (de)
English (en)
Other versions
EP1770281B1 (fr
EP1770281A3 (fr
Inventor
Dieter Roller
Gernot Balz
Thomas Varga
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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 Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP1770281A2 publication Critical patent/EP1770281A2/fr
Publication of EP1770281A3 publication Critical patent/EP1770281A3/fr
Application granted granted Critical
Publication of EP1770281B1 publication Critical patent/EP1770281B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • F04C29/026—Lubricant separation
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/902—Hermetically sealed motor pump unit

Definitions

  • the invention relates to a compressor for refrigerants, comprising an outer casing, a scroll compressor arranged in the outer casing with a first compressor housing fixedly arranged in the outer casing and a second compressor body movable relative to the first compressor body, each of which has a bottom and first or first floor rising above the respective bottom have second spiral ribs, which engage in one another such that for compressing the refrigerant, the second compressor body relative to the first compressor body on an orbital path about the central axis is movable, arranged in the outer housing drive unit for the second compressor body with an eccentric drive, a lying in the outer housing extending Drive shaft and a stator and a seated on the drive shaft rotor drive motor and a lubricant supply.
  • the invention is therefore an object of the invention to improve a compressor of the type mentioned in such a way that the smallest possible amount of lubricant is required.
  • a lubricant collection chamber is arranged, that the lubricant supply has a delivery wheel that promotes lubricant from a delivery sump in a supply space for the drive shaft and that in a winningsumpf receiving lubricant delivery space a lower pressure is present than in the lubricant collecting space, so that the lubricant collecting in the lubricant collecting space passes into the delivery sump due to the pressure difference.
  • the advantage of the solution according to the invention lies in the fact that the amount of lubricant in the delivery sump must not be ensured by a correspondingly large amount of lubricant in total, but that all accumulations of lubricant in the lubricant collection chamber are caused by the aid of the pressure difference between the lubricant collection chamber and the lubricant delivery space in the Conveying fuselage of the lubricant collection space and collect there to be conveyed by the feed wheel of the lubricant supply in the feed space.
  • a particularly favorable solution provides that the lubricant supply is arranged on a side of the drive motor opposite the spiral compressor.
  • the supply space could be arranged near the partition wall or at this.
  • a structurally particularly favorable solution provides that the supply space for the lubricant supply is arranged on an end wall of the outer housing.
  • a manufacturing technology particularly simple solution provides that the supply space is at least partially formed in the end wall.
  • a particularly simple embodiment of the compressor according to the invention provides that the conveying sump is arranged between the end wall of the outer housing carrying the feed space and the dividing wall.
  • the partition wall has a passage for lubricant from the lubricant collection chamber into the delivery sump.
  • the passage can be formed in various ways.
  • An advantageous solution provides that the passage comprises a lubricant receiving tube guided to a bottom side of the lubricant collecting space. As a result, the possibility is created to receive lubricant directly above the bottom side of the lubricant collecting space and to lead to the delivery sump in a particularly simple manner.
  • the lubricant collection tube extends to a central region of the lubricant collecting space, so that even with slight inclination of the drive shaft relative to a horizontal intake of lubricant collecting in the lubricant collecting space is ensured.
  • a bottom side of the lubricant collecting space is approximately parallel to a center axis of the drive shaft.
  • the lubricant collecting tube has an inlet opening facing the bottom side, which is arranged in particular at a small distance from the bottom side.
  • the feed wheel has a transversely to a disc plane of the feed wheel extending edge region.
  • the edge region is shaped like a groove to hold the lubricant as long as possible and deliver it into a centrifugal space of the lubricant delivery chamber, from which it is then fed via collecting walls to the feed space.
  • the drive motor can be cooled in various ways, for example, it is conceivable to cool the drive motor by the high-pressure compressed refrigerant.
  • Another advantageous solution provides to cool the drive motor by sucked refrigerant.
  • the drive motor is provided with a flow guide jacket, which leads refrigerant for cooling by the drive motor.
  • cooling effect it is particularly favorable when sucked in to a compressed from the flow guide casing engine interior, to be compressed refrigerant.
  • the Schmierstoffabscheideraum is disposed between the flow guide casing and the outer housing.
  • a favorable solution provides that the lubricant collecting space between the drive motor and the outer housing is arranged.
  • lubricant collecting space is arranged in a space between the flow guide casing of the drive motor and the outer casing.
  • the combination of the lubricant separation with the collection of the lubricant can be realized particularly favorable when the lubricant separation space in the space between the flow guide casing and the outer housing in the direction of gravity is arranged above the lubricant collecting space.
  • a particularly favorable solution provides that a lower static pressure is present in a suction space of the scroll compressor than in the lubricant collecting space.
  • Such a pressure gradient arises, for example, by a flow cross-sectional constriction when the refrigerant passes from the lubricant separation space into the suction space, wherein, for example, a static pressure in the lubricant separation space corresponds approximately to a pressure in the lubricant collection space.
  • Such a pressure gradient between the lubricant collection chamber and the suction chamber can be used in particular for generating a static pressure difference between the lubricant collection chamber and the lubricant delivery chamber.
  • a connection line leads from the suction space of the scroll compressor to the lubricant delivery space.
  • a pressure equalization between the lubricant delivery chamber and the suction chamber so that the static pressure in the lubricant delivery space is approximately equal to the static pressure in the suction, possibly slightly higher than this, but preferably always lower than the static pressure in the lubricant collection chamber.
  • a particularly favorable solution provides that the drive unit is mounted in a bearing unit, which is designed between the scroll compressor and the drive motor.
  • the bearing unit is designed so that it is supported in the outer housing.
  • the bearing unit is formed so that in the bearing unit passages for the passage of the refrigerant from the Schmierstoffabscheideraum are provided in the suction space of the scroll compressor.
  • an advantageous embodiment of the compressor according to the invention is constructed so that the drive shaft is supported by a second bearing unit, which is arranged on one of the first bearing unit opposite side of the drive motor.
  • a favorable constructive solution provides that the lubricant collecting space lies between the bearing units.
  • a first exemplary embodiment of a compressor according to the invention shown in FIGS. 1 and 2 comprises an outer housing designated as a whole by 10, which comprises a substantially cylindrical jacket 12 having a first cover 14 in the region of a first end and a first cover 14 in the region of a second end second lid 16 is closed.
  • a designated as a whole with 20 spiral compressor is provided on a side facing the first cover 14, which has a first, fixedly arranged in the outer housing 10 compressor body 22 and a second, movably arranged in the outer housing 10 compressor body 24, each over a bottom 26 and 28 elevating spiral ribs 30 and 32, respectively, which engage in such a way that for compressing refrigerant, the second compressor body 24 relative to the first compressor body 22 on an orbital path about a central axis 34 is movable.
  • the second compressor body 24 is still guided by a known Oldham coupling 36 relative to the stationarily arranged first compressor body 22.
  • the scroll compressor 20 is thereby driven by a drive unit designated as a whole by 40, which comprises a cam housing 44 fixedly connected to the second compressor body 24, preferably integrally formed thereon, on which an eccentric 46 rotating about the central axis 34 engages around the second compressor body 24 on the orbital path to move about the central axis 34.
  • a drive unit designated as a whole by 40 which comprises a cam housing 44 fixedly connected to the second compressor body 24, preferably integrally formed thereon, on which an eccentric 46 rotating about the central axis 34 engages around the second compressor body 24 on the orbital path to move about the central axis 34.
  • the eccentric 46 engages in a bore 48 formed by the eccentric receptacle 44 and abuts against it with outer circumferential surfaces 50. But it is also conceivable that the eccentric 46 surrounds the eccentric receptacle 44.
  • the eccentric 46 is formed on a designated as a whole with 52 drive shaft, which is rotatably mounted coaxially to the central axis 34 and extends approximately lying.
  • the drive shaft 52 is mounted in a first storage unit 54 facing the scroll compressor 20 and on an opposite side in a second storage unit 56, which faces the second cover 16.
  • Both bearing units 54 and 56 are supported directly or indirectly on the outer housing 10 and keep the drive shaft 52 lying substantially when the outer housing 10 is placed or mounted according to this provided on the mounting elements 58.
  • the jacket 12 also extends approximately parallel to the likewise lying central axis 34, in particular coaxially to this.
  • the drive shaft 52 is driven by a designated as a whole by 60 drive motor comprising a stator 62 arranged between the bearing units 54 and 56 and a disposed between the bearing units 54 and 56 rotor 64, wherein the rotor 64 sits directly on the drive shaft 52 and from this is rotatably mounted about the central axis 34.
  • stator 62 is held in a motor housing 66, which comprises a bearing on the bearing units 54 and 56 gas guide jacket 68 which carries the stator 62.
  • the gas guide casing 68 encloses a motor interior 70, which in the region of a first winding head 72 and a second winding head 74 has a first flow space 76 and a second flow space 78, wherein the first flow space 76 is located on one of the first bearing unit 54 side facing the motor interior 70 and the second flow space 78 is located on a side of the motor interior 70 facing the second storage unit 56.
  • gas guide casing 68 extends at a distance from the casing 12, so that between the casing 12 of the outer casing 10 and the gas guide casing 68 of the drive motor 60 forms a circumferential space 80 around the motor housing 66.
  • the cooling of the drive motor 60 is carried out now by the fact that via a suction port 82 of the compressor sucked refrigerant to be compressed is supplied directly to the engine interior 70, for example in the region of the second Umströmungsraums 78, while the second winding heads 74 cools, then at least partially a gap between the Rotor 64 and the stator 62 passes through and enters the first Umströmungsraum 76, in which a cooling of the first winding heads 72 takes place. From the first bypass space 76, the drawn-in refrigerant then exits the motor housing 66, preferably via an opening 84 provided in the gas guide jacket 68, and enters into the intermediate space 80.
  • a deflection of the same in two opposite azimuthal directions 86 and 88 to the central axis 34 through a flow guide 90 and also at the outlet of the sucked refrigerant from the interior 70 via the opening 84 is carried out by a in an intermediate space 80 provided Strömungsleitelement 92 a deflection in two with respect to the central axis 34 opposite Azimutalraumen 94 and 96, along which then the refrigerant flows in the gap 80, namely, as shown in Fig.
  • passages 102 and 104 which in an outer flange 106 of the first bearing unit 54 are provided, and through which the sucked refrigerant can enter into a suction chamber 110, which lies on a side facing the scroll compressor 20 side of the first bearing unit 54.
  • the suction space 110 is also enclosed by an end region 112 of the jacket 12 facing the first cover 14 and a curved intermediate base 114 which overlaps the first compressor body 22 and extends from the end region 112 of the jacket 12 to a high-pressure outlet 116 of the jacket 12 first compressor body 22 surrounding ring body 118 of the first compressor body 22 extends so that between the first compressor body 22 and the intermediate bottom 114 a up to the annular body 118 extending flow space 120 remains, through which a cooling of the first compressor body 22 on its side facing away from the first spiral ribs 30 side is possible.
  • the space 80 serves with its lying between the flow guide 92 and the passages 102 and 104 area as Schmierffenabscheideraum 122, wherein the deposited lubricant in the space 80 following gravity collects in a lying below the Schmierstoffabscheideraum 122 lubricant collection chamber 124.
  • the lubricant collection chamber 124 is additionally protected from the lubricant separation chamber 122 by shielding elements 126 and 128 against the ingested refrigerant, wherein the shielding elements 126 and 128 do not prevent the lubricant from entering the lubricant collection chamber 124 hinder.
  • the lubricant collection chamber 124 lies in a lower region of the intermediate space 80 in the direction of gravity, preferably on a side facing the mounting elements 58.
  • the gap 80 extends between the entirelyflansch Scheme 106 of the first bearing unit 54 and a second bearing unit 56 supporting partition wall 130, both of which extend in the radial direction to the central axis 34 to the shell 12 and terminate with this substantially tight.
  • a feed wheel 142 having a seated on one end 144 of the drive shaft 52 hub 146, on which a radially extending conveyor disc 148 is held ,
  • the conveyor disc 148 extends in a lying between the partition 130 and the second cover 16 lubricant conveying space 150, which includes a conveyor sump 152, in which collects lubricant to be conveyed, and a centrifugal space 154, in which of the feed wheel 142 from the conveyor sump 152 centrifugal lubricant is thrown off, wherein the centrifugal space 154 is preferably located on a side facing away from the conveyor sump 152 in the direction of gravity 152 of the lubricant delivery chamber 150.
  • the centrifugal space 154 is provided at least in a partial area of collecting walls 156 for the lubricant, which collect this and lead into a supply chamber 158, from which the lubricant can then be supplied to the drive shaft 52.
  • the cover 16 is provided with a bulge 160 which on the one hand forms the collecting walls 156 and on the other hand partially surrounds the feed space 158 in its region facing the central axis 34, this feed space 158 additionally being characterized by a between a lower region of the bulge 160 and the conveyor plate 148 lying boundary wall 162 is formed, so that the lubricant from in relation to the direction of gravity above the feed space 158 extending collecting walls 156 may enter the supply chamber 158.
  • a bulge 160 which on the one hand forms the collecting walls 156 and on the other hand partially surrounds the feed space 158 in its region facing the central axis 34, this feed space 158 additionally being characterized by a between a lower region of the bulge 160 and the conveyor plate 148 lying boundary wall 162 is formed, so that the lubricant from in relation to the direction of gravity above the feed space 158 extending collecting walls 156 may enter the supply chamber 158.
  • outlet pipe 164 which extends in the direction of the end 144 of the drive shaft 52 and projects into a lubricant receiving bore 166 in the end 144 of the drive shaft 52.
  • the drive shaft 52 from the end 144 to the eccentric 46 passes through lubricant delivery channel 170, which extends obliquely to the central axis 34 and with rotating drive shaft 52 due to the centrifugal force lubricant from the lubricant receiving bore 166 out promotes to lubricate a bearing 172, with which the drive shaft 52 is mounted in the second bearing unit 56, to lubricate a bearing 174, with which the drive shaft 52 is mounted in the first bearing unit 54, and to lubricate a bearing 176, which between the eccentric 46 and the eccentric receptacle 44 is provided.
  • the conveyor disc 148 In order to lose as little lubricant from the lubricant receiving bore 166, the conveyor disc 148 is formed so that its central opening 178 extends almost to an outer circumferential surface 180 of the outlet tube 164, so that only a narrow gap 182 between the outer circumferential surface 180 of the outlet tube 164 and forms the central opening 178 through which only a small amount of lubricant from the lubricant receiving bore 166 can escape into the lubricant supply chamber 150.
  • a seal 184 is inserted, which is effective between this and one of the partition 130 rear side facing 186 of the hub 146.
  • the lubricating oil delivery chamber 150 is substantially closed relative to the intermediate space 80 and the engine interior 70.
  • a lubricant receiving tube 190 penetrating the partition wall 130 which opens into the lubricant delivery chamber 150 in the region of the delivery sump 152 on the one side with an opening 192 and on the other side with an opening 194 in FIG the lubricant plenum 124, in the area near an inner surface of the outer casing 12 forming a bottom side 196 of the lubricant plenum 124, for receiving lubricant collecting above this bottom side 196, the bottom side 196 being approximately parallel to the central axis 34 of the drive shaft 52 and a lowest point of the lubricant collection space 124 represents.
  • the lubricant receiving tube 190 extends substantially to a region 198 which is approximately midway between the partition wall 130 and the Pureflansch Scheme 106 of the first bearing unit 54, even at an inclination of the bottom side 196 relative to a horizontal lubricant collecting in 124 in the lubricant collecting space over to accommodate the opening 194.
  • the opening 194 is disposed on a side facing the bottom side 196 so as to be able to receive directly above this accumulating lubricant without gaseous refrigerant being taken up with this lubricant.
  • the feed wheel 142 may be formed in the simplest case only by the conveyor disc 148.
  • the conveyor disc 148 which, as shown in Fig. 1, extending in a plane perpendicular to the central axis 34 disc plane 202 is provided with a radially outer trough-shaped outer edge 200, which is transverse to the disc plane 202 extending outer flange portion 204, and, as shown in Fig. 9, merges into a radially inwardly protruding annular portion 206 which terminates in a ring inner edge 208.
  • the lubricant conveyed by the feed wheel 142 can be collected by centrifugal force in an outer annular space 210, which the lubricant leaves due to the centrifugal force only in a centrifugal force lying in the direction of gravity above the central axis 34 centrifugal space 154 to be thrown against the collecting walls 156, the Then supply lubricant to the supply chamber 158.
  • the lubricant delivery space 150 is maintained at a static pressure level lower than the static pressure level in the lubricant collection chamber 124.
  • the static pressure level in the lubricant reservoir 124 corresponds to the pressure level in the gap 80 and the static pressure level in the gap 80 is higher than the static pressure level in the
  • the static pressure level in the lubricant supply chamber 150 is lowered relative to the pressure level in the lubricant collection chamber 124, through a connecting line 220 shown in FIG. 3, which passes through the partition wall 130 and from an opening 222 opening into the lubricant delivery chamber 150 to one in the Suction chamber 110 opening opening 224 is sufficient, so that via this connecting line 220, a pressure equalization between the lubricant supply chamber 150 and the suction 110 can be done and thus the static pressure in the lubricant supply chamber 150 can be kept lower than in the lubricant collection chamber 124.
  • the static pressure in the lubricant supply chamber 150th slightly above the static pressure of the suction chamber 110, so that due to the pressure difference, the lubricant always flows into the lubricant supply chamber 150 and forms in this the delivery sump 152, from which then the lubricant by the conveying errad 142 is conveyed into the supply chamber 158.
  • the compressed refrigerant preferably collects in a high-pressure space 230 which lies between the intermediate bottom 114 and the first lid 14 and exits from this high-pressure space 230 through a high-pressure connection 232.
  • the opening 222 opening into the lubricant delivery chamber 150 is covered by a hood 226, which forms a channel extending from the opening 222 and extending along the partition 130, which is one of the hub 146 the feed wheel 142 facing opening 228 through which takes place due to the lower static pressure in the suction chamber 110, a suction of gas from the lubricant supply chamber 150 via the duct formed by the hood 226 and via the connecting line 220.
  • the hood 226 has the advantage that it does not absorb gas from the lubricant delivery chamber 150 in the region of the centrifugal space 154, which is very heavily penetrated by lubricant droplets and / or lubricant mist, but from a region of the lubricant delivery chamber 150 near the hub 146, in which the proportion of lubricant droplets and lubricant mist is lower.
  • the second embodiment is formed in the same manner as the first embodiment, so that reference may be made to the comments on this full content.

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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)
EP06019416.4A 2005-09-30 2006-09-16 Compresseur pour fluide réfrigérant Active EP1770281B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005048093A DE102005048093A1 (de) 2005-09-30 2005-09-30 Kompressor für Kältemittel

Publications (3)

Publication Number Publication Date
EP1770281A2 true EP1770281A2 (fr) 2007-04-04
EP1770281A3 EP1770281A3 (fr) 2013-12-18
EP1770281B1 EP1770281B1 (fr) 2014-12-10

Family

ID=37654751

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06019416.4A Active EP1770281B1 (fr) 2005-09-30 2006-09-16 Compresseur pour fluide réfrigérant

Country Status (4)

Country Link
US (1) US7946831B2 (fr)
EP (1) EP1770281B1 (fr)
CN (1) CN100520075C (fr)
DE (1) DE102005048093A1 (fr)

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EP3734072A4 (fr) * 2017-12-25 2021-07-14 Toshiba Carrier Corporation Compresseur horizontal et dispositif à cycle frigorifique

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CN102367796A (zh) * 2011-04-28 2012-03-07 湖南华强电气有限公司 一种卧式涡旋压缩机主轴后端密封结构
FR2989433B1 (fr) 2012-04-16 2018-10-12 Danfoss Commercial Compressors Compresseur a spirales
CN105443377A (zh) * 2014-06-10 2016-03-30 丹佛斯（天津）有限公司 涡旋压缩机
CN111164352B (zh) * 2017-10-04 2022-07-12 比泽尔制冷设备有限公司 冷却剂压缩机设备
US11655820B2 (en) * 2020-02-04 2023-05-23 Aspen Compressor, Llc Horizontal rotary compressor with enhanced tiltability during operation

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US5345785A (en) * 1991-10-30 1994-09-13 Hitachi, Ltd. Scroll compressor and air conditioner using the same
EP1319840A1 (fr) * 1997-09-17 2003-06-18 SANYO ELECTRIC Co., Ltd. Compresseur à spirales

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GB2155549A (en) * 1984-03-13 1985-09-25 Mitsubishi Electric Corp Scroll compressor having improved lubricating structure
US5012896A (en) * 1989-02-17 1991-05-07 Empresa Brasileira De Compressores Lubricating system for rotary horizontal crankshaft hermetic compressor
US5345785A (en) * 1991-10-30 1994-09-13 Hitachi, Ltd. Scroll compressor and air conditioner using the same
EP1319840A1 (fr) * 1997-09-17 2003-06-18 SANYO ELECTRIC Co., Ltd. Compresseur à spirales

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3734072A4 (fr) * 2017-12-25 2021-07-14 Toshiba Carrier Corporation Compresseur horizontal et dispositif à cycle frigorifique
US11725660B2 (en) 2017-12-25 2023-08-15 Toshiba Carrier Corporation Horizontal compressor and refrigeration cycle system

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DE102005048093A1 (de) 2007-04-05
EP1770281B1 (fr) 2014-12-10
EP1770281A3 (fr) 2013-12-18
CN100520075C (zh) 2009-07-29
US20070077161A1 (en) 2007-04-05
CN1940302A (zh) 2007-04-04
US7946831B2 (en) 2011-05-24

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