EP1694964B1 - Kältemittelverdichter für kraftfahrzeuge - Google Patents

Kältemittelverdichter für kraftfahrzeuge Download PDF

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Publication number
EP1694964B1
EP1694964B1 EP04797850A EP04797850A EP1694964B1 EP 1694964 B1 EP1694964 B1 EP 1694964B1 EP 04797850 A EP04797850 A EP 04797850A EP 04797850 A EP04797850 A EP 04797850A EP 1694964 B1 EP1694964 B1 EP 1694964B1
Authority
EP
European Patent Office
Prior art keywords
drive shaft
lubricant
refrigerant compressor
accordance
compressor
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.)
Active
Application number
EP04797850A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1694964A1 (de
Inventor
Per Kaczmarek
Eike Hildebrandt
Günter DITTRICH
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
Priority to PL04797850T priority Critical patent/PL1694964T3/pl
Publication of EP1694964A1 publication Critical patent/EP1694964A1/de
Application granted granted Critical
Publication of EP1694964B1 publication Critical patent/EP1694964B1/de
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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F04B39/0253—Hermetic compressors with oil distribution channels in the rotating shaft using centrifugal force for transporting the oil

Definitions

  • the invention relates to a refrigerant compressor for motor vehicles comprising a compressor housing, at least two cylinder bores arranged in the compressor housing, pistons arranged in the cylinder bores, a drive shaft space arranged in the compressor housing, and a piston drive shaft arranged in the drive shaft space.
  • Such refrigerant compressors are from the US 2,427,638 known.
  • the refrigerant dissolving in the lubricant leads to a deterioration of the lubricating properties of the lubricant.
  • the invention is therefore based on the object to improve a refrigerant compressor of the type described above such that it can work with the lowest possible amounts of lubricant.
  • a lubricant conveyor a includes in the plenum engaging Schmierstoffschleuderusion which receives the lubricant from the plenum and promotes lubrication points, and which in the installation position substantially vertically.
  • the collecting space according to the invention which extends over only a part of the extent of the drive shaft space, it is possible to reduce the amount of lubricant required for a function of the lubricant delivery device, and thus likewise to reduce the problems associated with the known large quantities of lubricant.
  • the wall surfaces supply substantially all of the lubricant accumulating in the drive shaft space to the plenum so that it is ensured that lubricant does not collect in wells provided adjacent to the plenum that can not be received by the lubricant delivery means in these recesses would lead to an enlargement of the necessary Schmiermermerige.
  • the refrigerant compressor according to the invention can thus be used without problems in motor vehicles, since the collecting space always remains the lowest lying portion of the drive shaft section with a tilt of a drive shaft axis relative to the installation position to a maximum of plus / minus 15 °.
  • the solution according to the invention is particularly simple in that the lubricant delivery device comprises a lubricant centrifugal disk engaging in the collecting chamber, which essentially runs vertically in the installed position.
  • a particularly expedient solution provides that a part of the wall surfaces extends obliquely to a drive shaft axis of the piston drive shaft, in order thus to reduce the expansion of the collecting space in the direction of the drive shaft axis.
  • a particularly constructive executable solution provides that the collecting space adjacent to a housing cover of the compressor housing.
  • the housing cover is arranged such that it extends transversely to the drive shaft axis of the piston drive shaft.
  • the drive shaft space is in the installed position of the compressor in the direction of gravity below a cylinder space of the compressor housing.
  • the cylinder space is designed such that occurs in this accumulating lubricant substantially in the drive shaft space and thus form in the cylinder chamber substantially no additional collecting spaces, which retain the lubricant and thus contribute to an overall increase in the amount of lubricant, without the To improve lubrication of the refrigerant compressor according to the invention.
  • a structurally particularly favorable solution provides that the collecting space is formed in a drive shaft section of the compressor housing.
  • the wall surfaces which guide the lubricant to the collecting chamber are formed in the drive shaft section.
  • a structurally particularly expedient solution provides that the drive shaft section of the compressor housing forms a trough inclined towards the collecting chamber.
  • the collecting chamber always collects the lubricant at an inclination of the compressor housing to the drive shaft axis of the piston drive shaft to a maximum of plus / minus 90 °, in particular maximum plus / minus 45 ° relative to the mounting position.
  • Such Schmierstoffschleuderular could be driven by its own drive.
  • a particularly expedient solution provides that the Schmierstoffschleuderusion is driven by the piston drive shaft.
  • the lubricant centrifugal disc With regard to the arrangement of the lubricant centrifugal disc, no details have been given so far. For reasons of an advantageous overall design, it has proven to be expedient if the lubricant centrifugal disc is arranged near the compressor housing cover closest to the collecting space.
  • the lubricant delivery device is designed in the case of an intended Schmierstoffschleudermission such that it preferably has in the compressor housing a receiving space for thrown by the lubricant spinner disc lubricant.
  • the receiving space is preferably arranged so that it enters a lubricant projecting against a collecting surface and draining therefrom.
  • a particularly advantageous solution provides that the receiving space is arranged in the housing cover.
  • a further advantageous solution provides that the collecting surface is arranged on the housing cover.
  • the lubricant conveying means comprises guide ribs which direct the lubricant into the receiving space.
  • the supply of lubricant to at least a portion of lubrication points could be done for example by channels provided in the compressor housing.
  • the lubricant delivery device comprises a central lubricant channel integrated into the piston drive shaft.
  • a central lubricant channel of the piston drive shaft By such a central lubricant channel of the piston drive shaft, the individual lubrication points of the same can be very easily supplied with lubricant.
  • the supply of the central lubricant channel with lubricant can be structurally particularly realized when the central lubricant passage lubricant from the receiving space can be fed.
  • lubricant supply passages extending transversely to the central lubricant passage enhance lubricant delivery because centrifugal force acts on the lubricant in the lubricant supply passages by the rotation of the piston drive shaft, which then radially conveys it to the central lubrication channel to the respective lubrication points, thereby creating a pumping action.
  • the filling quantity of the lubricant is less than 1.5 times the displacement of the refrigerant compressor.
  • the object mentioned is also achieved by a refrigerant compressor of the type described above according to the invention that the piston drive shaft is mounted in the compressor housing only in plain bearings and that the plain bearings have lack lubricated sliding layers.
  • the plain bearings still have the advantage that they have an improved stability against vibrations, in particular standstill vibrations.
  • lubrication points with insufficient lubrication in the inventive solution, it is preferably provided that are mounted on the piston drive shaft drive elements for the pistons with plain bearings, which have lack lubrication sliding layers.
  • Such lack lubricating sliding layers can be provided, for example, on the piston drive shaft, for example eccentric bodies thereof.
  • These drive elements are, for example, connecting rods in whose connecting rod engaging on the piston drive shaft such sliding layers are provided.
  • the drive elements are mounted on the piston with plain bearings, which have lack lubrication sliding layers.
  • a piston pin could be provided with such a lack lubricating sliding layer.
  • a solution which is expedient with respect to the production provides that a connecting rod eye engaging the piston pin is provided with a lubricant-lubricious sliding layer.
  • the leadership of the piston usually requires lubrication.
  • Such lack lubricated leadership of the piston could be, for example, realize that the cylinder surfaces are provided with a lack lubricating sliding layer.
  • a structurally expedient solution provides that the pistons have lack lubricated piston rings, which can then run directly on the cylinder surfaces.
  • pistons in particular on the piston skirt, to be provided with lubricant layers that can be lubricated to a limited extent.
  • the refrigerant compressor according to the invention can still further advantageous form that in this the piston zylinderlaufbüchsenlitis on the compressor housing, that is essentially directly in cylinder bores of the compressor housing, are performed.
  • Under lubrication lubricious sliding layers is to be understood that in these lubrication with a lubricant for a defined period of time can be interrupted without damage occurring in the region of the respective plain bearing. In extreme cases, the lack lubricating sliding layers are designed such that they are dry-run, that is suitable for a longer period without lubricant for storage.
  • a particularly advantageous embodiment of such lack lubricative sliding layers provides that this PTFE, that is polytetrafluoroethylene include.
  • these lack lubricating overlays can be improved by incorporating stability-enhancing additives such as CaF into the PTFE.
  • a further advantageous solution provides that the lack lubricating sliding layers comprise a porous layer of sintered bronze, which also has good deficient lubrication properties.
  • a particularly favorable solution provides that is embedded in the porous layer of sintered bronze PTFE.
  • the piston drive shaft can be driven via a clutch, wherein the clutch is preferably designed as an electromagnetic clutch.
  • the drive element of the clutch in turn is mounted on the compressor housing via rolling bearings.
  • all lateral forces acting on the drive element act on the compressor housing via the rolling bearing, but to a significantly reduced extent, if at all, on the piston drive shaft.
  • the drive element can be any type of drive element for a clutch.
  • this may be a drive wheel, as well as, for example, a drive gear, for the clutch.
  • drive element in particular for use in motor vehicles, provides that the drive element is a pulley, in which considerable forces occur due to the belt tension.
  • the compressor housing 10 can be subdivided into a cylinder section 20 which, for example, has two cylinder banks 22 and 24 (FIG. Fig. 2 ), and in the installed position in the vertical direction below the cylinder portion 20 lying drive shaft portion 26 in which a designated as a whole by 30 piston drive shaft 30 is rotatably mounted about a drive shaft axis 32.
  • the storage of the piston drive shaft 30 takes place in the region of a first bearing 34, which is arranged in the housing body 12 on a side facing the housing cover 14 side, and a second bearing 36, which is arranged on the second housing cover 16.
  • the bearing 34 is formed by a preferably integrally formed on the housing body 12 first annular body 40, in which a first plain bearing bush 42 is used with a lack lubricating sliding layer 44, the piston drive shaft 30 in the plain bearing bush 42 with a first sliding surface 45 formed outer surface sliding is stored.
  • the first sliding surface 45 is provided in a first bearing portion 46 of the piston drive shaft 30.
  • the second bearing 36 is formed by a second annular body 50, which is integrally formed on the second housing cover 16.
  • a second plain bearing bush 52 with a poor-seeming sliding layer, in which the piston drive shaft 30 is mounted with a second sliding surface 55 formed as outer surface of a second bearing portion 56 of the piston drive shaft 30.
  • the piston drive shaft 30 is in turn provided for example with a first eccentric body 60 and a second eccentric body 62, wherein on the first eccentric body 60, a first connecting rod 64 and a second connecting rod 66 are mounted, while on the second body, a third connecting rod 68 and a fourth connecting rod 70th are rotatably mounted.
  • the third connecting rod 68 drives a piston 80 of the cylinder bank 24 while the fourth connecting rod 70 drives a piston 80 of the cylinder bank 22.
  • first connecting rod 64 drives a piston of the cylinder bank 24 and the second connecting rod 66 drives a piston of the cylinder bank 22.
  • Each of the connecting rods 64, 66, 68, 70 is mounted with its large connecting rod eye 82 in the form of a sliding bearing on the respective eccentric body 60, 62, while a small connecting rod eye 84 of the respective connecting rod is rotatably mounted via a piston pin 86 on the respective piston 80.
  • the storage of the small connecting rod eye 84 is formed on the piston pin 86 as a sliding bearing.
  • the large connecting rod eye 82 and the small connecting rod eye 84 are each provided with a deficient sliding layer 88.
  • Each of the pistons 80 is in turn, as in Fig. 2 shown, slidably guided in a cylinder-bearing surface 100 of a cylinder bore 98, and preferably at least via a piston ring 102, which is arranged in the piston skirt 104 near a piston crown 106. Furthermore, preferably takes place nor a guide of the respective piston 80 through an outer surface 108 of the piston skirt 104, which is arranged on a piston bottom 106 opposite side of the piston ring 102.
  • the piston ring 102 is preferably formed so that its outside 110 sliding on the cylinder surface 100 is formed by a PTFE-comprising material, for example, the cylinder surface 100 is formed as a machined and in particular hardened aluminum outer surface of the housing body 12 made of cast aluminum.
  • the outer surface 108 of the piston skirt 104 is provided with a sliding layer 112 comprising PTFE.
  • the piston 80 as a whole is guided in the cylinder bore 98 so that it can not be lubricated.
  • the cylinder bore 98 is then in turn completed by a valve plate 116 on which sit the valves not shown in the drawing, which in turn are covered by a cylinder head cover 118.
  • a clutch plate 130 is arranged as a whole with 132 designated electromagnetic clutch, the clutch plate 130 is held via a flexible ring 136 to a seated on the end portion 128 clutch hub 138 ,
  • the electromagnetic clutch 132 includes a drivable pulley 140, which in turn is rotatably supported by rolling bearings 142 on the lug 126 of the first housing cover 14.
  • the pulley 140 still includes a ring portion 144 to which the clutch plate 130 is frictionally applied, by an electromagnet 146 which is disposed on one of the clutch disc 130 opposite side of the ring portion 144 of the pulley 140 and stationary at the neck 126 is held.
  • the clutch disc 130 By energizing the electromagnet 146, the clutch disc 130 is pulled against the ring portion 144 of the pulley 140 and frictionally applied and thereby driven by the driven pulley 140, all acting by the belt drive on the pulley 140 unilateral and transverse to the drive shaft axis 32 forces from the rolling bearing 142 are received for the pulley 140.
  • the drive of the drive section 120 of the piston drive shaft 30 is effected by the clutch disc 130 via the flexible ring 136 and the clutch hub 138 free from external, in particular due to the belt drive transverse forces, so that in particular in the region of the first bearing 34 no such transverse forces must be taken.
  • the sliding layers 44, 54 are constructed so as to have a support body 150 made of steel, on which a porous layer 152 of sintered bronze is arranged, wherein in pores or interstices 154 of the layer 152 of sintered bronze, a material filling them 156, comprising PTFE (polytetrafluoroethylene) and additives introduced, for example, rolled so that on a sliding surface 158 of such sliding layers 44, 54, the porous layer 152 of sintered bronze together with the PTFE comprising material 156 is present together lack lubricatable or at least temporarily dry-run properties on the sliding surface 158, so that the respective abutting sliding surfaces 45, 55 can be guided and supported without wear for a considerable amount of time substantially without wear by the sliding surface 158 or on the sliding surface 158.
  • PTFE polytetrafluoroethylene
  • such a structure of a lack lubricated or dry-running sliding surface 158 is not only provided in connection with the sliding bearing layers 44 and 54, but also in the region of large Pleuelauges 82 and the small connecting rod 84 of the respective connecting rod 64, 66, 68, 70, as a sliding layer 88 and preferably also in the sliding layer 112 on the piston skirt 104 and in the formation of the piston ring 102nd
  • the lubricant conveyor 160 includes a lubricant spinner 162 which is rotatable coaxially with the drive shaft axis 32 with the spool drive shaft 30.
  • the Schmierstoffschleuderefficiency 162 is held on an imbalance balancing body 164 of the piston drive shaft 30 and is located near the second housing cover 16, wherein the Schmierstoffschleuderusion 162 engages the integrally formed on the second housing cover 16 annular body 50 of the second bearing 36 on its outer side ( Fig. 1 ).
  • the lubricant centrifugal disk 162 dips into a lubricant sump 166 which forms inside the compressor housing 10 and hurls the lubricant from the lubricant sump 166 against an inner side 168 of the second housing cover 16, wherein the inner side 168 ribs 170 extending radially to the drive shaft (FIGS. Fig. 5 . 6 7 ), between which opposite the ribs 170 recessed collecting surface 172 are arranged, which together with the ribs 170 in the second housing cover 16 recessed recessed collecting pockets 174 form, the collecting pockets 174 lie only between the ribs 170, the extend in the installed position of the refrigerant compressor in the vertical direction over the piston drive shaft 30.
  • the lubricant thrown by the lubricant spinner 162 into the collecting pockets 174 adheres at least partially to the collecting surfaces 172 and travels at the collecting surfaces 172 and optionally guided by the ribs 170 in the direction of the piston drive shaft 30 due to gravity.
  • the collecting surfaces 172 thereby extend into a receiving space 176 for the lubricant, which, as in Fig. 1 and 7 recognizable, facing in the second housing cover 16 of an end face 178 of the piston drive shaft and is arranged open to this.
  • lubricant supply channels 182 and 184 which in the sliding surfaces 45 and 55 lying mouth openings 186, 188, via which a lubrication of the sliding bearing of the sliding surfaces 45 and 55 on the sliding layers 44, 54 of the plain bearing bushings 42 and 52 takes place.
  • each in slide surfaces 200, 202, 204, 206 for the connecting rods 64, 66, 68, 70 outlet openings 210, 212, 214, 216 contribute to the lubrication of the large connecting rods 82 of the individual connecting rods 64, 66, 68, 70 slidably mounted on the sliding surfaces 200, 202, 204, 206 with their sliding layers 88 ( Fig. 1 ).
  • Lubrication in the region of the sliding layers 88 of the small connecting-rod eyes 84 and the sliding layers 112 and the piston rings 102 of the pistons 80 takes place by means of a lubricant mist generated by the lubricant centrifugal disk 162 in the compressor housing 10.
  • central lubricant channel 180 also branches off a lubricant supply channel 220, which serves to supply the mechanical seal 122 with lubricant.
  • the slide seal chamber 124 is formed in the lug 126 so as to collect and jam the lubricant leaking out of the mechanical seal 122, preferably the entire slide seal 122 is immersed in the lubricant accumulating in the seal seal chamber 124 and the lubricant is only has the possibility to leave the sliding ring sealing chamber 124 via an overflow channel 222 arranged above the first ring body 40.
  • the lubricant passing through the mechanical seal 122 becomes, as in FIG Fig. 8 shown, collected in a gap 125 between the mechanical seal 122 and an outer shaft seal 123 and fed via a channel 218 to a cavity 219.
  • the trough 228 is inclined with its wall surfaces 232 and the bottom surface 234 in the direction of the collecting space 230 in order to supply all, entering the trough 228 lubricant to the collecting space 230 by gravity.
  • the overflow from the overflow channel 222 from the mechanical seal chamber 124 lubricant passes around the first ring body 40 around in the trough 228 and is thereby fed to the plenum 230.
  • the lubricant collecting in the cavity 219 is also supplied via a channel 236 to the drive shaft space 226.
  • the collecting space 230 is preferably formed so that the lubricant collecting in it to form the lubricant sump 166, even with inclination of the drive shaft axis relative to the ideal mounting position by up to plus / minus 35 °, preferably up to plus / minus 15 ° in the vertical direction or Also, rotation of the compressor housing about the drive shaft axis 22 by up to plus / minus 90 °, preferably up to plus / minus 45 ° relative to the optimal mounting position still detected by the lubricant spinner 162 and can be thrown into the collecting pockets 174.
  • this lubricant Since lubricant is transported along with the refrigerant according to the invention, this lubricant, which has been transported with it, is also fed back, at least in part, via sucked-in refrigerant.
  • lubricant is also supplied via a suction gas channel 240 into the compressor housing.
  • the lubricant then settles in the central suction gas channel 240 and then enters the branch ducts 242, 244 leading to the cylinder banks 22, 24.
  • branch channels 242, 244 in turn, as in particular in Fig. 2 and Fig. 7 illustrated, collecting areas 246, 248, starting from which lubricant via discharge channels 250, 252 enter the cylinder chamber 224 and can be guided from there to the trough 228, so that in turn the lubricant supplied from the refrigerant to the refrigerant compressor can be collected in the plenum 230 ,
  • the refrigerant compressed in the refrigerant compressor flows via branch channels 256, 258 into a central compressed gas channel 260, from which it emerges from the compressor housing 10 via a compressed gas connection 262 ( Fig. 3 . 9 ).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Motor Or Generator Cooling System (AREA)
EP04797850A 2003-11-17 2004-11-12 Kältemittelverdichter für kraftfahrzeuge Active EP1694964B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL04797850T PL1694964T3 (pl) 2003-11-17 2004-11-12 Sprężarka czynnika chłodniczego do pojazdu mechanicznego

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10354529 2003-11-17
DE10358471A DE10358471A1 (de) 2003-11-17 2003-12-10 Kältemittelverdichter für Kraftfahrzeuge
PCT/EP2004/012839 WO2005050019A1 (de) 2003-11-17 2004-11-12 Kältemittelverdichter für kraftfahrzeuge

Publications (2)

Publication Number Publication Date
EP1694964A1 EP1694964A1 (de) 2006-08-30
EP1694964B1 true EP1694964B1 (de) 2009-06-24

Family

ID=34621310

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04797850A Active EP1694964B1 (de) 2003-11-17 2004-11-12 Kältemittelverdichter für kraftfahrzeuge

Country Status (10)

Country Link
US (1) US20060216176A1 (pl)
EP (1) EP1694964B1 (pl)
CN (2) CN100523499C (pl)
AT (1) ATE434726T1 (pl)
BR (1) BRPI0416682A (pl)
DE (2) DE10358471A1 (pl)
DK (1) DK1694964T3 (pl)
ES (1) ES2327531T3 (pl)
PL (1) PL1694964T3 (pl)
WO (1) WO2005050019A1 (pl)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006307700A (ja) * 2005-04-27 2006-11-09 Toyota Industries Corp 圧縮機
JP4905464B2 (ja) * 2007-09-10 2012-03-28 パナソニック株式会社 冷媒圧縮機
DE102008004569A1 (de) * 2008-01-10 2009-07-16 Bitzer Kühlmaschinenbau Gmbh Hubkolbenverdichter
DE102009006040A1 (de) * 2009-01-24 2010-07-29 Bock Kältemaschinen GmbH Verdichter
CN105004083A (zh) * 2014-04-18 2015-10-28 松下知识产权经营株式会社 涡轮机和制冷循环装置
JP6635414B2 (ja) * 2014-12-19 2020-01-22 パナソニックＩｐマネジメント株式会社 ターボ機械
JP6607376B2 (ja) * 2015-07-01 2019-11-20 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置
EP3440359B1 (de) * 2016-04-06 2020-10-07 BITZER Kühlmaschinenbau GmbH Kältemittelverdichtereinheit

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1012348A (en) * 1911-05-29 1911-12-19 John Gabrielson Curtain-fixture.
US1093387A (en) * 1912-11-27 1914-04-14 Steve Ducsay Sash-holder.
US1842303A (en) * 1930-04-25 1932-01-19 Wainwright Charles Air compressor
US2035276A (en) * 1932-05-05 1936-03-24 Copeland Refrigeration Corp Refrigerant compressing unit
US2017684A (en) * 1933-10-31 1935-10-15 Westinghouse Air Brake Co Fluid compressor
US2300973A (en) * 1941-08-29 1942-11-03 Gen Electric Compressor
US2427638A (en) * 1944-08-16 1947-09-16 Vilter Mfg Co Compressor
US3058451A (en) * 1961-03-10 1962-10-16 Eimco Corp Air motor assembly
US3189126A (en) * 1963-03-18 1965-06-15 Mack Trucks Engine crankcase
US3587406A (en) * 1968-07-26 1971-06-28 Copeland Refrigeration Corp Compressor
JPH10331769A (ja) * 1997-05-30 1998-12-15 Zexel Corp 冷媒圧縮機
DE19726943C2 (de) * 1997-06-25 2000-03-23 Bitzer Kuehlmaschinenbau Gmbh Kältemittelkompressor
DE19745662A1 (de) * 1997-10-17 1999-04-22 Bitzer Kuehlmaschinenbau Gmbh Kompressor
DE19918161A1 (de) * 1999-04-22 2000-11-02 Bitzer Kuehlmaschinenbau Gmbh Kältemittelverdichteranlage

Also Published As

Publication number Publication date
DK1694964T3 (da) 2009-08-31
DE10358471A1 (de) 2005-06-23
ES2327531T3 (es) 2009-10-30
PL1694964T3 (pl) 2009-12-31
CN100523499C (zh) 2009-08-05
ATE434726T1 (de) 2009-07-15
CN101363432B (zh) 2014-08-06
DE502004009671D1 (de) 2009-08-06
US20060216176A1 (en) 2006-09-28
BRPI0416682A (pt) 2007-02-13
CN1882780A (zh) 2006-12-20
CN101363432A (zh) 2009-02-11
WO2005050019A1 (de) 2005-06-02
EP1694964A1 (de) 2006-08-30

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