WO2009030536A1 - Compresseur d'agent de refroidissement - Google Patents

Compresseur d'agent de refroidissement Download PDF

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Publication number
WO2009030536A1
WO2009030536A1 PCT/EP2008/058259 EP2008058259W WO2009030536A1 WO 2009030536 A1 WO2009030536 A1 WO 2009030536A1 EP 2008058259 W EP2008058259 W EP 2008058259W WO 2009030536 A1 WO2009030536 A1 WO 2009030536A1
Authority
WO
WIPO (PCT)
Prior art keywords
electric drive
drive unit
height
compressor
refrigerant
Prior art date
Application number
PCT/EP2008/058259
Other languages
German (de)
English (en)
Inventor
Meinhard Falch
Franz Leitgeb
Original Assignee
Acc Austria Gmbh
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 Acc Austria Gmbh filed Critical Acc Austria Gmbh
Priority to CN200880111935XA priority Critical patent/CN101828036B/zh
Priority to US12/733,384 priority patent/US20110217189A1/en
Priority to EP08774425.6A priority patent/EP2185819B1/fr
Publication of WO2009030536A1 publication Critical patent/WO2009030536A1/fr

Links

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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • 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
    • F04B39/0094—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 crankshaft
    • 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
    • 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
    • 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
    • F04B39/122—Cylinder block
    • 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
    • F04B39/125—Cylinder heads
    • 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
    • F04B39/127—Mounting of a cylinder block in a casing
    • 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
    • F04B39/128—Crankcases

Definitions

  • the present invention relates to a refrigerant compressor comprising an electric drive unit, a cylinder housing, a crankshaft driven by the electric drive unit, and a crankshaft driven in the
  • the present invention further relates to a family of refrigerant compressors of different refrigerating capacity, each refrigerant compressor comprising an electric drive unit, a cylinder housing, a crankshaft driven by the electric drive unit, and a cylinder-driven, refrigerant-compressing piston driven by the crankshaft the electric drive unit of each refrigerant compressor of the family depending on the cooling capacity has a different height.
  • Such refrigerant compressors are well known and are mainly used in the household sector, such as refrigerators or freezers. They are arranged in a hermetically sealed outer housing and part of a refrigerant circuit in which the refrigerant compressor compresses a gaseous refrigerant which is supplied from an evaporator of the piston / cylinder unit. When compressing the refrigerant pressure and temperature increase. As a result, the refrigerant is transferred in a condenser in the liquid state and finally fed through an expansion valve to the evaporator, where it evaporates again. The necessary heat of vaporization is removed from the environment or a cold room, which is thereby cooled. Finally, the gaseous refrigerant from the evaporator is returned to the piston / cylinder unit and undergoes a new compression and expansion cycle.
  • refrigerant compressors with different cooling capacities are offered.
  • the component which essentially determines the cooling capacity of a refrigerant compressor is the electric drive used.
  • the displacement and thus the piston size vary as well as the hub itself and thus contribute to different cooling capacities.
  • the overall height of a refrigerant compressor is essentially determined by the height of the electric drive unit and the height of the mounted on the electric drive unit cylinder housing. While the overall height of the cylinder housing is kept constant in general and only the cylinder diameter and the cylinder stroke varies slightly depending on the cooling capacity, the height of the electric drive unit varies significantly depending on the cooling capacity.
  • the electric drive unit is usually a single-phase asynchronous motor, which consists of a rotor and a stator together with winding packages, wherein the stator is formed as a laminated core, which significantly affects the height of the electric drive unit, as will be explained in more detail below .
  • the refrigerant compressor itself is arranged in a hermetically sealed outer housing, into which a suction line opens, which leads the refrigerant to the cylinder, and from which a pressure line leads away, which conducts the compressed refrigerant to the condenser. Furthermore, there is a connection flange for electrical lines on the hermetically sealed housing to supply the drive unit with electricity inside.
  • an oil sump for lubricating the moving parts of the refrigerant compressor.
  • the oil is conveyed to the lubrication points due to the rotation of the crankshaft itself, which for this purpose has two sections provided with different oil conveying means (oil delivery spindle, eccentric bore).
  • compressor family Several refrigerant compressors with a large number of identical components are referred to as the compressor family.
  • the individual members of a compressor family differ from each other by the cooling capacity and / or by the efficiency and thus mainly by the electric drive unit used.
  • Outer housing, crankshaft, cylinder housing, etc. are therefore identical or nearly identical (exceptions: cylinder bore diameter, stroke, and various mounting exemptions), to allow economic production.
  • the height compensation elements In addition to maintaining the overall height of the refrigerant compressors within a family of compressors, however, the height compensation elements also allow to always use identical crankshafts for each member of a compressor family by keeping the cylinder housing, which has the main bearing for the crankshaft always equidistant from the bottom of the outer casing , regardless of the height of the between cylinder housing and bottom of the outer housing arranged electric drive unit. Thus, the same length crankshafts can always be used. Without the height compensation, shorter crankshafts would have to be used due to the smaller distance between the cylinder housing and the bottom of the outer housing in refrigerant compressors with smaller electric drive units.
  • the main bearing in particular the lower main bearing has to be sufficiently high inside the housing for housing the larger electric drive unit, between main bearings of the crankshaft and oil sump.
  • the located below the lower main bearing portion of the crankshaft must therefore have sufficient length to still be able to immerse in the oil sump at the bottom of the outer housing in order to promote the oil to the lubrication points.
  • a refrigerant compressor with an electric drive unit, a cylinder housing, driven by the electric drive unit crankshaft and driven by the crankshaft, guided in the cylinder housing, the refrigerant-compressing piston that between the cylinder housing and the electric drive unit at least one height compensation element is arranged.
  • the cylinder housing has at least one contact flange, which is fastened to at least one corresponding contact surface of the electric drive unit, wherein the at least one height compensation element is arranged between the contact flange and the contact surface.
  • the electric drive unit is a single-phase synchronous motor and in the contact area around the laminated core of the stator of the single-phase synchronous motor.
  • each refrigerant compressor of the compressor family in a compressor family, each refrigerant compressor of the compressor family, an electric drive unit, a cylinder housing, driven by the electric drive unit crankshaft and driven by the crankshaft , guided in the cylinder housing, the refrigerant-compressing piston comprises and wherein the electric drive unit of each refrigerant compressor of the compressor family depending on the cooling capacity and efficiency from the height of the electric drive unit and from the height of the cylinder housing (without height compensation elements) composed different height, is provided that at least one height compensation element angeor between the electric drive unit and the cylinder housing of each refrigerant compressor dnet is.
  • the distance between the lower edge of the height defining portion of the electric drive and the axis of the cylinder housing in each compressor can be set substantially identical and the overall height can be kept constant and it is possible to grow the electric drive unit up toward the cylinder housing and at the same time the main camp as deep as possible in the vicinity to arrange the oil sump.
  • the dimensioning of the main bearing length can then take place in this case due to the largest electric drive unit and so the bearing load and friction losses are minimized within a compressor family.
  • the section defining the overall height of the electric drive is the height of the laminated core of the stator.
  • Fig.l a refrigerant compressor according to the prior art in isometric view
  • FIG. 5 shows a schematic view of a refrigerant compressor according to the prior art according to Figure 3
  • FIG 6 shows a schematic view of a refrigerant compressor according to the prior art according to FIG 7 shows a crankshaft in detail
  • FIG. 8 shows a schematic view of a refrigerant compressor according to the invention with a small drive unit
  • FIG. 9 shows a schematic view of a refrigerant compressor according to the invention with a larger drive unit
  • FIG. 10 shows an isometric view of a refrigerant compressor according to the invention
  • FIG. 11 is an isometric view of a height compensation element according to the invention
  • Fig. 14 is an isometric view of an alternative embodiment of a height compensation element according to the invention.
  • Fig. 1 shows a refrigerant compressor according to the prior art in an isometric view consisting of a cylinder housing 1 and an electric drive unit, of which in Fig.l the laminated core 2 and the winding heads 3a, 3b are shown schematically, and height compensation elements of which the spiral spring elements 4th are visible, which also serve for an elastic storage of the refrigerant compressor.
  • the outer housing in Fig.l was not drawn.
  • the cylinder housing 1 has a plurality of contact flanges 5, which extend in the direction of the crankshaft axis 6 and stand up on the Bleckbeck 2. Cylinder housing 1 and laminated core 2 are not fixed to each other in Fig.l screws connected to each other, which penetrate from below the laminated core 2 and end present in the Aufstandflanschen 5, having a threaded holes.
  • FIG. 2 shows a sectional view of a refrigerant compressor according to Fig.l including the outer housing 10, which is composed of two hermetically sealed housing halves 10a, 10b. 2 also shows the crankshaft 11 which drives the piston 12 via a connecting rod 13.
  • the crankshaft 11 is mounted in a section of the cylinder housing 1 designated as the main bearing 14 and is preferably fastened to a rotor 15 of the electric drive unit by means of a press fit.
  • FIG. 2 shows a connection flange 16 fastened to the outer housing 10 for electrical lines, a suction muffler 17 arranged on the cylinder head and support feet 19, which serve for fixing the outer housing 10 to an external contact area.
  • FIG. 3 shows a sectional view of a prior art refrigerant compressor with the upper half of the outer case 10a omitted. Well visible now are the holes 7 in the laminated core 2 and in the risers 5, and the screws extending therein, which serve to connect the laminated core 2 and the cylinder housing 1.
  • the overall height Hi of the refrigerant compressor is composed of the height H z i of the cylinder housing 1, which extends from the lowermost end of the contact flanges 5 to the piston axis 24, and the height of the electric drive unit, which is determined by the height H. e i of the laminated core 2, which is why subsequently laminated core and electric drive unit are used synonymously.
  • the outer housing 10 is matched to the refrigerant compressor such that the upper housing half 10a runs just above the cylinder housing 1 and runs down in the region of the electrical connection flange 16 in the direction of the same.
  • the outer housing of a compressor family is always dimensioned after that refrigerant compressor with the greatest power.
  • height compensation elements are provided, for example in the form of support elements 8 and 9, which are surrounded by a spiral spring element 4, which are arranged below the electric drive unit 2, for example, on the underside of the laminated core 2 and on which the refrigerant compressor superimposed.
  • the height of a height compensation element is thus composed of the total height of the support elements 8, 9, including the surrounding spiral spring element 4, which is set under load by the refrigerant compressor.
  • FIG. 4 shows a refrigerant compressor of the same type as in the prior art but with a lower cooling capacity. This is recognizable on the one hand at the lower height H e2 of the laminated core 2 and the lower due to the different bore diameter height H z2 of the cylinder housing 1 and thus a lower overall height H 2 .
  • height compensation elements constructed of the support elements 8,9 and the spiral spring elements 4, of the same type as described in Fig. 3, are provided, but with the difference that they have a greater height H h2 than the height H h i of the height compensation elements forming components 4, 8, 9 in Figure 3.
  • FIG. 5 shows a purely schematic view of a prior art refrigerant compressor according to FIG. 3 with the largest electric drive unit 2 of a compressor family and FIG. 6 with the smallest electric drive unit 2 of the same compressor family.
  • main bearing length H L and bearing width B L are identical in both cases, so that the larger electric drive unit 2 of Figure 5 reduces the distance between the compressor and the oil sump 19, since the total height H Ges of the refrigerant compressor so limited by the height of the outer housing is.
  • the main bearing length H L of this compressor could be increased and thus the bearing load can be reduced or retained the bearing load but the friction losses can be reduced.
  • the press fit length P L of the attachment of the rotor 15 to the crankshaft 11 would then be smaller in this case, but would still be sufficiently dimensioned or in other words the press fit length P L in Figure 5 is unnecessarily large and it would be advantageous the main bearing length H. L to increase the bearing forces and to achieve smaller friction losses. If, however, the main bearing length H L were to be increased, the required smallest possible interference fit length P L min could not be maintained for smaller compressors of the same compressor family as shown in FIG.
  • the oil head H oe i (without immersion depth E t ) to the lower main bearing 18 is therefore unnecessarily high in known refrigerant compressors to provide space for the largest electric drive unit 2 a compressor family, although, as shown in Figure 6, the lower main bearing 18th could be arranged closer towards oil sump 19.
  • Fig.7 shows, for better understanding, a crankshaft in
  • the oil between ⁇ leinhoffsbohrung 21 and lower main bearing 18 is conveyed via an eccentric bore within the crankshaft 11, wherein the delivery height, ie the distance between the oil inlet bore 21 and main bearing 18 is limited and depends inter alia on the diameter of the crankshaft 11.
  • FIGS. 5 and 6 show purely schematically a refrigerant compressor according to the invention, which differs from the prior art refrigerant compressors shown in FIGS. 5 and 6 in that at least one height compensation element 26 according to the invention is arranged between the cylinder housing 1 and the electric drive unit 2 and the compressor bearing elements 25 in each refrigerant compressor of the same family of compressors are always identical in terms of their height H h3 , so that the distance between the lower Surface of the stator 2 to the bottom of the outer housing 10 is always the same.
  • the height compensation elements 26 are provided.
  • Such a refrigerant compressor according to the invention can only grow upward due to the arrangement of the height compensation elements 26, ie. a larger electric drive unit 2 does not reduce the distance between the lower surface of the stator core 2 and the bottom of the outer housing 10.
  • FIG. 9 also shows purely schematically such a refrigerant compressor with the largest electric drive unit of a compressor family.
  • Height compensation elements 26 are not provided in this case, since the larger electric drive unit 2 has bridged this distance and grown upwards.
  • the lower main bearing 18 can therefore be arranged as far as possible in the outer housing 11, since only care must be taken that the compressor during operation, especially when starting does not touch the outer housing wall 10.
  • the main bearing length H L can be dimensioned on the basis of the largest electric drive unit 2 as shown in FIG. 9, since the press fit length P L is always the same regardless of the size of the electric drive unit 2.
  • the bearing load of each compressor of a compressor family can be reduced.
  • 10 shows an isometric view of a refrigerant compressor according to the invention, including height compensation elements 26, of which one can be seen by way of example in FIG. 11 in a detailed view. It can be seen from the above that the height compensation element 26 shown by way of example in FIG. 11 can have a different shape and that the illustrated shape is only one of many possible embodiments. An alternative embodiment, for example, Fig.12 or Fig.14.
  • FIG. 13 shows a sectional view through an inventive height compensation element 26 in the mounted position.
  • Fig. 14 shows an isometric view of an alternative embodiment of an inventive
  • Height compensation element 26 without bore but with clearance for receiving the connecting screw.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

La présente invention concerne un compresseur d'agent de refroidissement comprenant une unité d'entraînement électrique (2), un carter cylindre (1), un vilebrequin (11) qui peut être entraîné par l'unité d'entraînement électrique, et un piston (12) qui est entraîné par le vilebrequin (11), se déplace dans le carter cylindre (1) et comprime l'agent de refroidissement. Pour donner à la longueur de palier principal une dimension maximale, au moins un élément de compensation de hauteur (26) est disposé entre le carter cylindre (1) et l'unité d'entraînement électrique (2).
PCT/EP2008/058259 2007-08-28 2008-06-27 Compresseur d'agent de refroidissement WO2009030536A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN200880111935XA CN101828036B (zh) 2007-08-28 2008-06-27 致冷剂压缩机
US12/733,384 US20110217189A1 (en) 2007-08-28 2008-06-27 Refrigerant compressor
EP08774425.6A EP2185819B1 (fr) 2007-08-28 2008-06-27 Compresseur d'agent de refroidissement

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATGM515/2007 2007-08-28
AT0051507U AT10065U1 (de) 2007-08-28 2007-08-28 Kältemittelkompressor

Publications (1)

Publication Number Publication Date
WO2009030536A1 true WO2009030536A1 (fr) 2009-03-12

Family

ID=39494819

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/058259 WO2009030536A1 (fr) 2007-08-28 2008-06-27 Compresseur d'agent de refroidissement

Country Status (5)

Country Link
US (1) US20110217189A1 (fr)
EP (1) EP2185819B1 (fr)
CN (1) CN101828036B (fr)
AT (1) AT10065U1 (fr)
WO (1) WO2009030536A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011154428A2 (fr) 2010-06-08 2011-12-15 Arcelik Anonim Sirketi Compresseur hermétique
WO2011154430A2 (fr) 2010-06-08 2011-12-15 Arcelik Anonim Sirketi Compresseur hermétique

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BRPI1101247A2 (pt) * 2011-03-18 2013-05-14 Whirlpool Sa mola de suspensço para um compressor de refrigeraÇço
JP6469575B2 (ja) * 2013-09-03 2019-02-13 パナソニック アプライアンシズ リフリジレーション デヴァイシズ シンガポール 密閉型圧縮機およびそれを搭載した冷蔵庫または冷凍装置
WO2017137328A1 (fr) * 2016-02-09 2017-08-17 Arcelik Anonim Sirketi Compresseur à fonctionnement silencieux
CN113048037B (zh) * 2019-12-26 2024-01-05 安徽美芝制冷设备有限公司 压缩机和制冷设备
CN113048038B (zh) * 2019-12-26 2023-09-19 安徽美芝制冷设备有限公司 压缩机和制冷设备
CN113864156B (zh) * 2021-10-28 2023-01-17 珠海格力电器股份有限公司 一种往复式压缩机

Citations (4)

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Publication number Priority date Publication date Assignee Title
DE3134218A1 (de) 1980-12-10 1982-07-22 VEB dkk Scharfenstein, DDR 9366 Scharfenstein Hermetischer kaeltemittelverdichter
EP0507091A1 (fr) 1991-03-26 1992-10-07 Whirlpool Europe B.V. Ensemble moteur-compresseur hermetique avec un chassis ou support d'appui amélioré de moteur
US20040057850A1 (en) 2002-09-20 2004-03-25 Tsutomu Nozaki Hermetic type compressor
AT8188U1 (de) * 2004-11-02 2006-03-15 Acc Austria Gmbh Kältemittelverdichter

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AT407208B (de) * 1998-01-28 2001-01-25 Verdichter Oe Ges M B H Wickelkopf
US6171076B1 (en) * 1998-06-10 2001-01-09 Tecumseh Products Company Hermetic compressor assembly having a suction chamber and twin axially disposed discharge chambers
BR0200039A (pt) * 2002-01-09 2003-10-28 Tecumseh Do Brasil Ltda Aperfeiçoamentos em compressor hermético para sistema de refrigeração com aplicação veicular
JP4337635B2 (ja) * 2004-05-28 2009-09-30 パナソニック株式会社 密閉型圧縮機
DE102004028747A1 (de) * 2004-06-14 2005-12-29 Obrist Engineering Gmbh Hubkolbenkompressor
CN1769674A (zh) * 2004-11-05 2006-05-10 乐金电子(天津)电器有限公司 多气缸密闭型压缩机
DE102004054186B3 (de) * 2004-11-10 2006-06-14 Danfoss Compressors Gmbh Kompressor-Kurbelwelle

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3134218A1 (de) 1980-12-10 1982-07-22 VEB dkk Scharfenstein, DDR 9366 Scharfenstein Hermetischer kaeltemittelverdichter
EP0507091A1 (fr) 1991-03-26 1992-10-07 Whirlpool Europe B.V. Ensemble moteur-compresseur hermetique avec un chassis ou support d'appui amélioré de moteur
US20040057850A1 (en) 2002-09-20 2004-03-25 Tsutomu Nozaki Hermetic type compressor
AT8188U1 (de) * 2004-11-02 2006-03-15 Acc Austria Gmbh Kältemittelverdichter

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011154428A2 (fr) 2010-06-08 2011-12-15 Arcelik Anonim Sirketi Compresseur hermétique
WO2011154430A2 (fr) 2010-06-08 2011-12-15 Arcelik Anonim Sirketi Compresseur hermétique
CN102939698A (zh) * 2010-06-08 2013-02-20 阿塞里克股份有限公司 密封压缩机
CN103038583A (zh) * 2010-06-08 2013-04-10 阿塞里克股份有限公司 密封压缩机

Also Published As

Publication number Publication date
CN101828036B (zh) 2013-07-03
US20110217189A1 (en) 2011-09-08
EP2185819B1 (fr) 2016-12-07
EP2185819A1 (fr) 2010-05-19
AT10065U1 (de) 2008-08-15
CN101828036A (zh) 2010-09-08

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