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EP0183332B1 - Ansaugrohrdichtung für Rotationsverdichter - Google Patents

Ansaugrohrdichtung für Rotationsverdichter Download PDF

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Publication number
EP0183332B1
EP0183332B1 EP19850304276 EP85304276A EP0183332B1 EP 0183332 B1 EP0183332 B1 EP 0183332B1 EP 19850304276 EP19850304276 EP 19850304276 EP 85304276 A EP85304276 A EP 85304276A EP 0183332 B1 EP0183332 B1 EP 0183332B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
housing
suction tube
compressor
aperture
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.)
Expired
Application number
EP19850304276
Other languages
English (en)
French (fr)
Other versions
EP0183332A1 (de
Inventor
Edwin L. Gannaway
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.)
Tecumseh Products Co
Original Assignee
Tecumseh Products Co
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 Tecumseh Products Co filed Critical Tecumseh Products Co
Publication of EP0183332A1 publication Critical patent/EP0183332A1/de
Application granted granted Critical
Publication of EP0183332B1 publication Critical patent/EP0183332B1/de
Expired legal-status Critical Current

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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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators

Definitions

  • This invention pertains to hermetic rotary compressors for compressing refrigerant in refrigeration systems such as air conditioners, refrigerators, and the like.
  • the invention relates to the manner of sealing the suction tube to the cylinder in a rotary hermetic compressor.
  • prior art hermetic rotary compressors comprise a housing which is hermetically sealed. Located within the housing are an electric motor and a compressor mechanism. The electric motor is connected to a crankshaft which has an eccentric portion thereon. The eccentric portion of the crankshaft is located within a bore of the compressor cylinder. A roller located within the bore is mounted on the eccentric portion of the crankshaft and is driven thereby. The roller cooperates with a sliding vane to compress refrigerant within the bore of the cylinder.
  • Rotary hermetic compressors of the type herein disclosed generally have a pressurized or high side sealed housing.
  • the compressor is connected into a refrigeration circuit by means of suction and discharge tubes.
  • the motor stator may be secured to the interior wall of the housing by shrink fitting and the compressor cylinder is generally welded to the housing.
  • a motor rotor is journalled in a bearing and drives the crankshaft.
  • the suction tube extends through the housing and is sealingly connected thereto.
  • the end of the suction tube which extends into the housing is connected to the cylinder and conducts low pressure refrigerant directly to the cylinder bore for compression therein.
  • the connection of the suction tube to the cylinder is usually made by press fitting or swaging the tube into an aperture in the cylinder wall. To that end, the suction tube outside diameter is made larger than the inside diameter of the cylinder aperture so that a good friction fit can be achieved.
  • the tolerances to which the cylinder, roller and vane must be manufactured are generally very exacting, such as 0.254 mm (ten thousandths of an inch).
  • the reason for such very tight tolerances is that leakage of refrigerant in compressors must be minimized in order to achieve acceptable efficiencies of the compressor pumps. Since the assembly operations of welding the cylinder to the housing and pressing or swaging the suction tube into the cylinder aperture tend to distort the cylinder, thereby causing vane slot distortion and misalignment between the cylinder and the bearing, the prior art cylinders have generally been designed with a relatively large axial dimension so as to be of relatively heavy construction.
  • the press fitted suction tube is surrounded by sufficient cylinder material so that distortion is minimized, vane slot geometry and alignment of the bearings are preserved, and close tolerances are maintained. If distortion were not minimized and the dimensional tolerances could not be held during the welding and swaging operations, leakage in the compressor would become excessive.
  • the sealed connection of the suction tube to the suction muffler was made by means of an 0 ring.
  • the O ring did not provide a sealing connection between compressor areas of high pressure differentials such as the suction and discharge gas areas.
  • this prior art compressor was of the reciprocating rather than the rotary variety so that there was no need for a thin cylinder to which the suction tube had to be sealingly connected and in which a large pressure drop existed across the sealed connection.
  • the prior art solution to the problem of providing a suitable sealed suction tube connection to the cylinder in a high side rotary compressor by using a thick cylinder and having the suction tube pressed therein has the disadvantage that it tends to increase the length of the refrigerant leakage paths and heat transfer surface thereby tending to decrease the efficiency of the compressor.
  • the bore of the compressor cylinder has both an inlet portion at suction pressure and a high pressure portion wherein the gas is compressed.
  • the compressor housing itself is at high pressure because compressed refrigerant is expelled from the cylinder bore directly into the housing.
  • the height of the cylinder is a critical dimension affecting leakage since it is directly related to the border length dividing the high and low pressure areas in the compressor cylinder bore. For instance, the length of the tip of the sliding vane which contacts the roller and the cracks between the vane and vane slot form a border dividing the high and low pressure cylinder bore areas. By using a thin cylinder this critical dimension can be kept small and the refrigerant leakage past the vane as well as other borders can be reduced.
  • the present invention overcomes the disadvantages of the above described prior art hermetic rotary compressors by providing an improved sealed connection between the suction tube and the compressor cylinder.
  • the suction tube extends through the compressor housing and is secured to the housing wall.
  • the diameter of the suction tube end which extends into the housing is made slightly smaller than the diameter of the aperture in the cylinder which receives this suction tube end.
  • An annular groove surrounds the aperture and receives a flexible O ring. The 0 ring seals the suction tube end slidably to the cylinder, so that the suction tube can slide within the aperture and can move axially with respect to the cylinder aperture as the housing flexes.
  • An advantage of this structure is that by making a sliding sealed connection between the suction tube and the cylinder by means of an 0 ring arrangement, a thin cylinder can be used because no distortion forces will be placed on the cylinder during the assembling of the suction tube thereto.
  • the use of a cylinder which has a small axial dimension reduces the lengths of the leakage paths formed by the borders dividing the low and high pressure areas of the compressor. For instance, the tip area of the sliding vane which contacts the roller and cracks in the vane slot are relatively small if the height of the compressor is relatively small. Thus, the amount of refrigerant which can leak from the high pressure side of the bore to the low pressure side of the bore past the vane tip and flanks are reduced, whereby the efficiency of the compressor is improved.
  • Another advantage is the elimination of special fittings for sealing the suction tube to the cylinder as well as the elimination of the swaging or pressing operation for securing the suction tube to the cylinder.
  • a further advantage is that by the elimination of the pressing or swaging operation the possibility of distortion of the compressor cylinder is eliminated and better bearing alignment and slot geometry are maintained, thereby decreasing leakage in the compressor and reducing excessive wear of the bearings.
  • a method of attaching a suction tube to a housing during the assembly of a compressor which comprises an electric motor secured to an inside wall of the housing; a crankshaft within the housing rotatably connected to the motor; a cylinder located inside the housing and connected to the inside wall thereof, the cylinder having a compression chamber therein; a piston means operably connected to the crankshaft for compressing refrigerant within the chamber; discharge means in the cylinder in operative association with the chamber for discharging compressed refrigerant; an aperture in the cylinder wall communicating with the compression chamber; adaptor means having a first cylindrical portion connected to a second, wider cylindrical portion by a connection portion, the second cylindrical portion being sealingly connected to the housing with the first cylindrical portion projecting radially outwards from the housing; a suction tube having an end extending through the adaptor means into the housing, the tube being sealingly connected to the first cylindrical portion and the end being received within the aperture; and flexible sealing means interposed between the wall of the aperture and the tube wall for sealing the tube
  • FIG. 1 there is shown a side sectional view of the compressor with the compressor disposed horizontally.
  • a casing or housing 10 is shown having a cylindrical portion 12 and top and bottom portions 14 and 16, respectively.
  • a flange 18 is shown welded to the bottom portion of the compressor. The flange is used for mounting the compressor when it is assembled to a refrigeration apparatus such as an air conditioner or refrigerator.
  • a terminal cluster 20 is provided for making electrical connections from a supply of electric power to the compressor motor.
  • a discharge tube 22 extends through the top portion of the housing and into the interior of the compressor as shown. The tube is sealingly connected to the housing as by soldering.
  • a suction tube 24 extends into the interior of the compressor housing as further described hereinbelow. The outer end of suction tube 24 is connected to an accumulator 26 which has support plates 28 disposed therein for supporting a filtering mesh 29.
  • An electric motor 30 is disposed within the compressor housing and includes a stator 31 and a rotor 32.
  • the electric motor is an induction type of motor having a squirrel cage rotor. Windings 33 provide the rotating magnetic field for inducing rotational movement of the rotor.
  • the cylindrical stator 31 is secured by interference fit to the interior wall of the housing 10 as by shrink fitting. In the shrink fitting process the housing 10 is heated so that it expands. Motor stator 31 is then inserted and positioned and the assembly is allowed to cool. As the assembly cools, the housing 10 will shrink and will securely grasp the motor stator 31.
  • a crankshaft 34 is secured to the hollow interior aperture of the rotor 32 by shrink fitting.
  • the crankshaft 34 extends axially through an upper bearing 36, and a cylinder 37 into a lower or outboard bearing 38.
  • the crankshaft is journalled in sleeve bearings 35 and 39.
  • the main bearing 36 has three flanges 40 thereon for securing the bearing to the housing 10 at points 41 such as by welding.
  • the main bearing 36 comprises a relatively long sleeve bearing portion 35 for journalling or rotatably supporting crankshaft 34.
  • Lower bearing 38 has a sleeve bearing portion 39 for journalling the end portion of crankshaft 34.
  • Cylinder 37 and lower bearing 38 are secured to main bearing 36 by means of six bolts 50 as best illustrated in Figs. 1 and .2.
  • Bolts 50 extend through holes 51 in the main bearing and holes 44 in the cylinder block and are threaded into the lower bearing 38.
  • the six bolts 50 could be replaced with twelve bolts, six of which would secure outboard bearing 38 to the cylinder and be threaded into the cylinder. The remaining six bolts would secure main bearing 36 to the cylinder and be threaded into the cylinder.
  • crankshaft 34 has an eccentric portion 52 thereon for revolving eccentrically around the crankshaft axis.
  • a cylindrical roller member 54 surrounds the eccentric and rolls around circular bore 55 as the eccentric revolves around the crankshaft axis.
  • a counterweight 56 for counterbalancing the eccentric 52 is secured to the end ring 57 of the motor rotor such as by riveting.
  • a rectangular sliding vane 58 is received in a vane slot 59.
  • the vane slot 59 is located in the cylinder wall of cylinder 37.
  • a spring 60 biases the end of vane 58 against the roller 54 for continuous engagement therewith.
  • the spring 60 is received in a spring pocket 62 machined into the wall of the cylinder.
  • a lubrication hole 64 in shaft 34 communicates with lubrication passage 66 in outboard bearing 38.
  • Passage 66 receives oil from a lubrication pump 68 disposed centrally in shaft 34. The oil is pumped upwardly by centrifugal force through the central opening in the shaft and is spun outwardly into radial passage 66 in outboard bearing 38.
  • Shaft 34 has an annular opening (not shown) machined therein for communication of pump aperture 68 with passage 66.
  • An oil passage 70 is provided adjacent vane 58 for lubricating the vane.
  • a radial oil lubrication hole 73 is provided in eccentric 52 of shaft 34 for lubricating the roller 54.
  • the hole 73 communicates with pump aperture 68 in shaft 34 and receives oil therefrom.
  • Another aperture 74 is provided in cylinder 37 to accommodate the rectangular end of vane 58..
  • the end portion of the suction tube end 24 within the housing 10 is received within an aperture 90 in the cylinder wall. Since it is desirable to have a thin cylinder 37 as explained hereinabove, the height or axial dimension of cylinder 37 is chosen to be small. Therefore, the amount of material of cylinder 37 surrounding the aperture 90 in the axial direction of cylinder 37 is relatively small. This material is indicated at numerals 92 and 94 in Figure 4. Cylinder 37 is preferably constructed of cast iron which is somewhat porous. The porosity of the cylinder material determines the minimum dimension of the thickness of the material surrounding the aperture 90 such as portions 92 and 94 since it is desired to prevent leakage of any refrigerant through the walls of the cylinder 37.
  • the thickness of the cylinder material surrounding the aperture 90 is made too small, compressed refrigerant might escape through the pores of the cylinder material.
  • the minimum material thickness to prevent leakage has been found to be thirty-seven thousandths of an inch (0.925 mm). If this dimension is chosen to be smaller, the likelihood of leakage is increased due to the porosity of the material.
  • the inside diameter of the aperture 90 is greater than the outside diameter of suction tube 24.
  • Tube 24 is not frictionally engaged by the cylinder walls but is slidable inside aperture 90.
  • Aperture 90 communicates with the bore of the cylinder and includes a shoulder portion 96 to prevent tube 24 from entering too far into the aperture.
  • the tube end portion 100 also has a reduced diameter portion 98 at its end to aid the entry of tube 24 into aperture 90 during assembly.
  • Aperture 90 is encircled by a circular recess 102.
  • Recess 102 has a sealing ring 104 located therein.
  • the sealing ring 104 may be an 0 ring constructed of a flexible material or any other suitable flexible sealing ring.
  • the material for the O ring should be resistant to oil as the compressor contains lubricating oil, which will contact sealing ring 104.
  • Bunham which is an oil resistant neoprene rubber.
  • the suction tube 24 is not fastened into the aperture 90 but is in frictional engagement with O ring 104 and is slidably received within the aperture.
  • the suction tube 24 is secured to the compressor housing by being attached to a suction tube adapter 106 as by soldering.
  • Adapter 106 is cylindrical in shape and has a frusto-conical section 108.
  • the lower portion 110 of adapter 106 is spaced away from suction tube 24 so that a void or space 112 exists between portion 110 and suction tube 24.
  • Lower portion 110 is soldered to an upstanding flange 111 of housing 10.
  • a thin compressor cylinder 37 can be used.
  • the leakage paths between vane 58, roller 54 and cylinder vane slots 59 are thus kept at a minimum.
  • the efficiency of the compressor is thereby greatly improved over the efficiency of prior art structures.
  • heat transfer between cylinder 37 and the refrigerant gas is greatly reduced, thus further improving the efficiency of the compressor.
  • a rotary hermetic compressor of simple construction having a high side housing 10 and a thin cylinder 37 and having a high degree of efficiency by the utilization of a very effective seal 104 between the suction tube 24 and the cylinder 37.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Claims (4)

1. Verfahren zum Anschließen einer Saugleitung (24) an ein Gehäuse (10) während des Zusammenbaus eines Kompressors, der einen Elektromotor (30) umfaßt, der seinerseits an einer Innenwand (12) des Gehäuses (10) befestigt ist, eine Kurbelwelle (34) innerhalb des Gehäuses, drehbar mit dem Motor (30) verbunden, einen Zylinder (37), der sich innerhalb des Gehäuses (10) befindet und an dessen Innenwand angeschlossen ist, und der eine Druckkammer (55) aufweist, einen Kolben (52, 54), die mit der Kurbelwelle in Triebverbindung stehen, zum Komprimieren von in der Kammer befindlichem Kühlmittel, einem an die Kammer (55) angeschlossenen Auslaß (76) im Zylinder (37) zur Abgabe von komprimiertem Kühlmittel, einer mit der Druckkammer in Verbindung stehender Bohrung (90) in der Zylinderwand, einem Adapter (106) mit einem ersten, zylindrischen Abschnitt (106), der an einem zweiten, weiteren zylindrischen Abschnitt (110) mittels eines Übergangsabschnittes (108) angeschlossen ist, wobei der zweite zylindrische Abschnitt (110) dichtend an das Gehäuse (10) angeschlossen ist und der erste zylindrische Abschnitt radial aus dem Gehäuse hervorragt, mit einem sich durch den Adapter (106) in das Gehäuse (10) hinein erstreckenden Ende (100) der Saugleitung (24), wobei die Saugleitung (24) dichtend an den ersten zylindrischen Abschnitt angeschlossen ist, und wobei sich das Ende (100) in der Bohrung (90) befindet, und mit einer Dichtung (104), die zwischen der Wand der Bohrung (90) und der Leitungswand angeordnet ist, um das Leitungsende (100) in bezug auf den Zylinder (37) abzudichten, gekennzeichnet durch die Schritte des dichtenden Anschließens des zweiten zylindrischen Abschnittes (110) an das Gehäuse, und durch nachfolgendes dichtendes Verbinden des ersten zylindrischen Abschnittes mit der Saugleitung (24) durch Löten, wobei ein einteiliger zylindrischer Endabschnitt (100) der Saugleitung (24) durch den Adapter (106) eingeführt und in gleitenden Eingriff mit einem umgebenden Dichtungsring innerhalb der Bohrung (90) gebracht wird.
2. Verfahren nach Anspruch 1, dadurch gekennzeichnet, daß die Dichtung einen O-Ring (104) aus ölbeständigem flexiblem Werkstoff umfaßt.
3. Verfahren nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der zweite zylindrische Abschnitt (110) durch Löten dichtend an das Gehäuse (10) angeschlossen ist.
4. Verfahren nach einem der vorausgehenden Ansprüche, dadurch gekennzeichnet, daß die Bohrung (90) in radialer Richtung durch die Zylinderwand hindurchgeführt ist.
EP19850304276 1984-11-13 1985-06-14 Ansaugrohrdichtung für Rotationsverdichter Expired EP0183332B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US67030684A 1984-11-13 1984-11-13
US670306 2000-09-26

Publications (2)

Publication Number Publication Date
EP0183332A1 EP0183332A1 (de) 1986-06-04
EP0183332B1 true EP0183332B1 (de) 1989-05-31

Family

ID=24689878

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19850304276 Expired EP0183332B1 (de) 1984-11-13 1985-06-14 Ansaugrohrdichtung für Rotationsverdichter

Country Status (10)

Country Link
EP (1) EP0183332B1 (de)
JP (1) JPS61118576A (de)
CN (1) CN1003318B (de)
AU (1) AU591878B2 (de)
BR (1) BR8505076A (de)
CA (1) CA1246508A (de)
DE (1) DE3570720D1 (de)
DK (1) DK519585A (de)
MX (1) MX162604A (de)
PH (1) PH22760A (de)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4889475A (en) * 1987-12-24 1989-12-26 Tecumseh Products Company Twin rotary compressor with suction accumulator
US4888962A (en) * 1989-01-06 1989-12-26 Tecumseh Products Company Suction accumulator strap
US4969804A (en) * 1989-03-08 1990-11-13 Tecumseh Products Company Suction line connector for hermetic compressor
US5683235A (en) * 1995-03-28 1997-11-04 Dresser-Rand Company Head port sealing gasket for a compressor
JPH09310693A (ja) * 1996-05-22 1997-12-02 Sanyo Electric Co Ltd 密閉型圧縮機
JPH09324777A (ja) * 1996-06-05 1997-12-16 Sanyo Electric Co Ltd 密閉型ロータリ圧縮機
JP3932519B2 (ja) * 1997-06-06 2007-06-20 三菱電機株式会社 スクロ−ル圧縮機
JPH116479A (ja) * 1997-06-18 1999-01-12 Matsushita Electric Ind Co Ltd 密閉型圧縮機
EP1359324B1 (de) * 1998-12-15 2007-03-14 Matsushita Electric Industrial Co., Ltd. Hermetischer Verdichter
JP2003097447A (ja) * 2001-09-26 2003-04-03 Mitsubishi Electric Corp 密閉圧縮機
JP3728227B2 (ja) * 2001-09-27 2005-12-21 三洋電機株式会社 ロータリコンプレッサ
JP4251239B2 (ja) * 2007-07-25 2009-04-08 ダイキン工業株式会社 密閉式圧縮機
JP5056399B2 (ja) * 2007-12-20 2012-10-24 パナソニック株式会社 密閉型圧縮機
CN103782039B (zh) * 2011-11-08 2016-07-06 松下电器产业株式会社 压缩机
CN113883764B (zh) * 2021-11-08 2023-03-10 广东美芝制冷设备有限公司 储液器、压缩机组件及制冷设备

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2214086A (en) * 1938-12-31 1940-09-10 Gen Motors Corp Refrigerating apparatus
US2373909A (en) * 1941-09-25 1945-04-17 Gen Motors Corp Refrigerating apparatus
US3031861A (en) * 1959-03-13 1962-05-01 Alex A Mccormack Compressor unit for refrigeration system
US3209991A (en) * 1963-12-16 1965-10-05 Westinghouse Electric Corp Sealed compressor unit assembly
JPS505914B1 (de) * 1970-05-29 1975-03-08
US3871800A (en) * 1974-03-11 1975-03-18 Gen Electric Hermetically sealed compressor suction tube assembly
DE2650937C3 (de) * 1976-11-08 1981-12-10 Danfoss A/S, 6430 Nordborg Kältemaschine mit federnd in einer Kapsel gehaltenem Motorverdichter
JPS599189B2 (ja) * 1981-02-26 1984-02-29 ジューキ株式会社 ミシンの布制御装置
JPS58176486A (ja) * 1982-04-09 1983-10-15 Hitachi Ltd 密閉形電動圧縮機

Also Published As

Publication number Publication date
PH22760A (en) 1988-12-12
AU4914085A (en) 1986-05-22
CN1003318B (zh) 1989-02-15
JPS61118576A (ja) 1986-06-05
EP0183332A1 (de) 1986-06-04
MX162604A (es) 1991-05-31
CA1246508A (en) 1988-12-13
DE3570720D1 (en) 1989-07-06
CN85107168A (zh) 1986-10-29
DK519585A (da) 1986-05-14
BR8505076A (pt) 1986-07-29
DK519585D0 (da) 1985-11-12
AU591878B2 (en) 1989-12-21

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