US20230031688A1 - Hermetically encapsulated refrigerant compressor - Google Patents

Hermetically encapsulated refrigerant compressor Download PDF

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Publication number
US20230031688A1
US20230031688A1 US17/757,577 US202017757577A US2023031688A1 US 20230031688 A1 US20230031688 A1 US 20230031688A1 US 202017757577 A US202017757577 A US 202017757577A US 2023031688 A1 US2023031688 A1 US 2023031688A1
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US
United States
Prior art keywords
nozzle
cylinder head
cylinder
refrigerant
sound absorber
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.)
Abandoned
Application number
US17/757,577
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English (en)
Inventor
Erwin Berger
Ulf PLATZER
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.)
Anhui Meizhi Compressor Co Ltd
Original Assignee
Anhui Meizhi Compressor Co Ltd
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 Anhui Meizhi Compressor Co Ltd filed Critical Anhui Meizhi Compressor Co Ltd
Assigned to ANHUI MEIZHI COMPRESSOR CO., LTD. reassignment ANHUI MEIZHI COMPRESSOR CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BERGER, ERWIN, PLATZER, Ulf
Publication of US20230031688A1 publication Critical patent/US20230031688A1/en
Abandoned 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
    • 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
    • F04B39/0027—Pulsation and noise damping means
    • 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
    • F04B39/121—Casings
    • 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
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
    • 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
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0066—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using sidebranch resonators, e.g. Helmholtz resonators
    • 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
    • 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

Definitions

  • the present invention relates to hermetically encapsulated refrigerant compressors of the reciprocating compressor type, and in particular to such compressors for refrigerating machines used in household appliances such as refrigerators, freezers and small air conditioners.
  • Conventional hermetically encapsulated refrigerant compressors comprise a cylinder formed in a cylinder block and having an open end, a reciprocating piston arranged in the cylinder, a valve plate with a suction valve and a discharge valve, with the valve plate being attached to the cylinder block at the open end of the cylinder, a cylinder head located above the valve plate and defining a cylinder head space around the side of the valve plate facing away from the cylinder, the cylinder head having a cylinder head cover comprising an inlet for refrigerant to be drawn in and an outlet for compressed refrigerant.
  • Sound absorbers designed for drawing in refrigerant are an important component of the refrigerant compressor. Their tasks are to guide the refrigerant, to dampen noise caused by the refrigerant being drawn in periodically and to thermally insulate the refrigerant sucked into the cylinder against the environment. In doing so, the size of the sound absorber, in particular its length, shape and internal volume, has a very strong effect on the performance of the compressor. Due to the current trend of keeping the dimensions of these compressors, in particular their height, as small as possible, the size of the sound absorbers is also forcibly restricted, which can have a negative impact on the performance of the compressor.
  • refrigerant compressors have a reciprocating piston axis perpendicular to the valve plate, whereby the inlet opening for the refrigerant in the valve plate is located transversely to the axis of the reciprocating piston.
  • Refrigerant compressors are usually installed in devices in such a way that the axis of the reciprocating piston is arranged essentially horizontally.
  • conventional sound absorbers In order to connect the sound absorber to the inlet opening of the valve plate, conventional sound absorbers have a duct for discharging the refrigerant that has been drawn in, the duct having a deflection so that two duct sections being at an angle to one another are formed.
  • the duct can be connected to the inlet opening of the valve plate and, on the other hand, the sound absorber can be arranged opposite to the inlet opening at a distance and in an angularly offset manner in order to optimally utilize the available installation space. Accordingly, the duct section of the sound absorber that abuts the inlet opening of the valve plate is aligned at right angles to the valve plate. Since the sound absorber generally cannot be arranged on a level with the cylinder head cover due to lack of space, the above-mentioned deflection and the second duct section, which extends from the sound absorber and runs perpendicularly to the reciprocating piston axis, are provided.
  • the sound absorber can be arranged at a place below the cylinder block.
  • a reciprocating compressor with a sound absorber designed in this way is disclosed, for example, in patent application US 2009/0038329 A1, in particular in FIG. 4.
  • Refrigerant is drawn in from the sound absorber through the duct and conducted to the suction valve of the valve plate.
  • a few disadvantages are created, which will be explained in further detail below.
  • a significant disadvantage is caused by the deflection of the duct. Due to this deflection, the refrigerant is directed to the outer edge of the duct by the centrifugal force and impinges only a small area of the inlet opening of the suction valve. As a result, it is more difficult for the refrigerant to pass through the inlet opening, which can lead to a backlog of refrigerant and, consequently, to performance losses of the compressor.
  • a refrigerant compressor which has a hermetically encapsulated housing, a cylinder formed in a cylinder block and having an open end, a reciprocating piston arranged in the cylinder, a valve plate having a suction valve opening with a suction valve and a discharge opening with a discharge valve, and a cylinder head on the side of the valve plate facing away from the cylinder, the cylinder head defining a cylinder head space above the valve plate, which space is divided by a wall formed in the cylinder head into a suction chamber and a discharge chamber above a portion of the valve plate which contains the discharge valve.
  • thermal insulation means are provided which either are designed as a lining of the interior of the cylinder head with a thermally insulating material, such as, e.g., a heat-insulating film, or consist of a separate insert in the form of a hollow body, which also serves for sound insulation and is arranged in the interior of the cylinder head with minimum contact points.
  • the hollow body is arranged in the cylinder head space of the cylinder head, as a result of which its volume is inevitably small and sound absorption is therefore low.
  • the thermal insulation is also relatively low in this refrigerant compressor.
  • a refrigerant compressor is to be provided which overcomes the above-mentioned disadvantages of the prior art and allows quiet operation even in case of a small size.
  • the present invention achieves the given objects by providing a hermetically encapsulated refrigerant compressor of the reciprocating compressor type having the features of claim 1 .
  • Advantageous embodiments of the invention become apparent from the dependent claims, the specification and the drawings.
  • the present invention provides a hermetically encapsulated refrigerant compressor comprising a cylinder formed in a cylinder block and having an open end, a reciprocating piston arranged in the cylinder and having a reciprocating piston axis along which the reciprocating piston reciprocates, a valve plate comprising a suction valve opening and a discharge valve, the valve plate being attached to the cylinder block at the open end of the cylinder, a cylinder head on the side of the valve plate facing away from the cylinder, the cylinder head defining a cylinder head space at least above a portion of the valve plate which contains the discharge valve, the cylinder head comprising a cylinder head cover which has an outlet for compressed refrigerant, and a sound absorber.
  • a nozzle is arranged as an inlet for refrigerant to be drawn in, the nozzle having a first end arranged at the suction valve opening and a second end opposite to the first end.
  • the nozzle is inclined at a maximum angle of inclination of between ⁇ 45° and +45° in relation to the reciprocating piston axis.
  • the sound absorber is arranged outside of the cylinder head and has a housing that defines a cavity. A suction opening for refrigerant to be drawn into the cavity and a discharge opening for refrigerant to be discharged from the cavity are formed in the housing.
  • the nozzle passes through the cylinder head cover or is arranged outside of the cylinder head space, with the second end of the nozzle leading to the cavity of the sound absorber through the discharge opening.
  • a short suction path can be implemented, which, in comparison to the prior art, is designed without a right-angled deflection, whereby the occurrence of turbulences and flow losses is significantly reduced or even completely prevented.
  • the short suction path has the advantage that, on the one hand, material for the production of the sound absorber can be saved and, on the other hand, complex forming processes, which are necessary for creating the deflections of the ducts of conventional sound absorbers, can be omitted.
  • the refrigerant compressor can be manufactured more easily and quickly due to the simplified design, whereby production costs are reduced.
  • the refrigerant flows evenly through the entire cross-section of the nozzle and is thus conducted into the entire area of the suction valve opening. A backlog of refrigerant can thus be avoided, which means that refrigerant can be drawn into the cylinder more efficiently.
  • a particular advantage of the invention is that the sound absorber can be arranged on a level with the cylinder head cover, as a result of which the cavity in the sound absorber can be dimensioned on a comparatively large scale even if the compressors are small. Intake noises can thus be dampened better so that a quiet operation of the refrigerant compressor can be achieved.
  • the nozzle is designed as a pipe section or a conical hollow body.
  • the nozzle can have a curved or kinked design, with the maximum angle of inclination of any portion of the nozzle ranging between ⁇ 45° and +45° in relation to the reciprocating piston axis. Due to the inclination of the nozzle or portions of the nozzle which is comparatively low or non-existent in comparison to the prior art, the suction path is short and turbulences and flow losses in the nozzle remain low, whereby it is ensured that sufficient refrigerant is drawn in at any time.
  • the nozzle is designed in one piece with the cylinder head cover. This embodiment provides advantages due to a simple manufacturing process of the cylinder head cover with the nozzle, e.g., by a die-casting or injection process, and minimizes temperature stresses in the cylinder head cover.
  • the cylinder head cover and the nozzle are preferably made of a metal or a metal alloy, in particular aluminium or an aluminium alloy, or of a synthetic material, which optionally is fibre-reinforced.
  • the housing of the sound absorber is made of a synthetic material. This embodiment exhibits a particularly good thermal insulation of the refrigerant against the environment.
  • the nozzle has a shape which essentially corresponds to the cross-sectional area of the suction valve opening, in particular, however, an essentially circular or elliptical shape.
  • the discharge opening is arranged in a top side or a bottom side of the housing of the sound absorber.
  • the wall of the top side or, respectively, the bottom side of the housing must be inclined accordingly in this embodiment so that the nozzle can lead to the discharge opening of the housing.
  • FIG. 1 is a sectional view of a hermetically encapsulated refrigerant compressor with a cylinder head cover comprising a nozzle according to the present invention.
  • FIG. 2 shows a perspective view of the refrigerant compressor depicted in FIG. 1 .
  • FIG. 3 shows a perspective view of the cylinder head cover integral with the nozzle.
  • FIGS. 1 and 2 show a hermetically encapsulated refrigerant compressor 1 according to the invention.
  • the refrigerant compressor 1 comprises a cylinder 3 formed in a cylinder block 2 and having an open end, a reciprocating piston 4 arranged in the cylinder 3 , a valve plate 5 comprising a suction valve opening 6 and a discharge valve 7 , the valve plate being attached to the cylinder block 2 at the open end of the cylinder 3 , and a cylinder head 8 located above the valve plate 5 and defining a cylinder head space 9 around the side of the valve plate 5 facing away from the cylinder 3 .
  • the reciprocating piston 4 has a reciprocating piston axis 4 a along which the reciprocating piston 4 reciprocates.
  • the cylinder head 8 has a cylinder head cover 10 which has an inlet for refrigerant to be drawn in and an outlet for compressed refrigerant.
  • a sound absorber 12 is connected to the inlet of the cylinder head cover in that the inlet for refrigerant to be drawn in is formed in the cylinder head cover 10 as a nozzle 11 passing through the cylinder head cover 10 , with a first end 11 a of the nozzle 11 being arranged at the suction valve opening 6 and a second end 11 b of the nozzle 11 protruding from the cylinder head cover 10 .
  • the cylinder head 8 could also be configured such that it covers only a portion of the valve plate 5 , said portion containing the discharge valve 7 .
  • the nozzle 11 can pass through the cylinder head cover 10 , but it could also be arranged outside of the cylinder head space 9 , i.e., to the side, above or below the cylinder head cover 10 .
  • the nozzle 11 can be designed in one piece with the cylinder head cover 10 .
  • the nozzle 11 and the cylinder head cover 10 can be designed as separate components. It is also possible to design the nozzle 11 in several parts, with a one-piece design being preferred.
  • the nozzle 11 is designed as a straight pipe section and has a longitudinal axis 11 c which can be arranged at an angle of inclination a of between ⁇ 45° and +45° in relation to the reciprocating piston axis 4 a , wherein the angle of inclination a between the longitudinal axis 11 c of the nozzle 11 and the reciprocating piston axis 4 a is 0° in the illustrated exemplary embodiment, i.e., the nozzle 11 is arranged in parallel to the reciprocating piston axis 4 a .
  • a coaxial arrangement of the nozzle 11 in relation to the reciprocating piston axis 4 a is also provided in alternative embodiments of the invention.
  • the nozzle 11 could also be designed as a conical hollow body and/or could have a curved or kinked design, with the maximum angle of inclination a of each portion of the nozzle 11 in relation to the reciprocating piston axis 4 a also being between ⁇ 45° and +45° in such an embodiment.
  • the sound absorber 12 has a housing 12 a defining a cavity 12 d .
  • a suction opening 12 b for refrigerant to be drawn into the cavity 12 d and a discharge opening 12 c for refrigerant to be discharged from the cavity 12 d are formed.
  • the discharge opening 12 c is arranged in a side wall of the housing 12 a of the sound absorber 12 .
  • the discharge opening 12 c is in this case located in the upper half, more precisely in this exemplary embodiment in the upper third of a side wall of the housing 12 a of the sound absorber 12 .
  • the second end 11 b of the nozzle 11 leads through the discharge opening 12 c into the cavity 12 d of the sound absorber 12 , wherein, in the illustrated embodiment, the second end 11 b of the nozzle 11 protrudes through the discharge opening 12 c of the sound absorber 12 into the cavity 12 d of the sound absorber.
  • the first end 11 a of the nozzle 11 rests directly on the suction valve opening 6 of the valve plate 5 .
  • the nozzle 11 preferably has a shape adapted to the cross-sectional area of the suction valve opening 6 , e.g., a substantially circular or elliptical shape or combinations thereof.
  • the nozzle 11 can be shaped like a mouth, as can be seen in FIG. 3 , wherein the ends 11 a , 11 b of the nozzle 11 can each be shaped differently from one another.
  • the first end 11 a of the nozzle 11 can have a mouth-shaped design
  • the second end 11 b can have a circular design.
  • the cylinder head cover 10 and the nozzle 11 are preferably designed as an integral unit, which can be produced by injection moulding, for example. If the nozzle 11 and the cylinder head cover 10 are designed separately, the cylinder head cover 10 can be connected to the nozzle 11 by means of a non-positive connection, e.g., a press fit, or by screw threads or gluing.
  • the material of the nozzle 11 is preferably a metal or a metal alloy, e.g., aluminium or an aluminium alloy, but can also be another material known from the prior art, such as, e.g., a synthetic material, which optionally is fibre-reinforced.
  • the cylinder head cover 10 is preferably made of the same material as the nozzle 11 .
  • the sound absorber 12 is arranged at the second end 11 b of the nozzle 11 which is opposite to the valve plate 5 , wherein the nozzle 11 can be several centimetres, e.g. up to 10 cm, long and can protrude from the cylinder head cover 10 for a length of several centimetres, e.g. up to 5 cm.
  • the second end 11 b of the nozzle 11 which faces away from the valve plate 5 is thereby arranged at the discharge opening 12 c of the sound absorber 12 and has a shape of its external surface which is adapted to the contour of the discharge opening 12 c , whereby the second end 11 b of the nozzle 11 can be inserted through the discharge opening 12 c of the housing 12 a of the sound absorber 12 into the cavity 12 d of the housing 12 a of the sound absorber 12 in an essentially sealing manner.
  • the sound absorber 12 is preferably connected to the nozzle 11 by means of a non-positive connection, in particular by means of a press fit, in such a way that a tight connection is created.
  • this connection can be established by attaching the sound absorber 12 to the nozzle 11 .
  • the sound absorber 12 can also be integrally bonded to the nozzle 11 , e.g., by gluing or welding, in which case the sound absorber 12 and the nozzle 11 are preferably made of the same material.
  • the material of the sound absorber 12 is preferably a synthetic material.
  • the sound absorber 12 is shown schematically as having a simple cuboid shape.
  • the sound absorber 12 can, of course, also have other shapes, which, on the one hand, result from the shape of the other parts of the refrigerant compressor 1 and, on the other hand, are configured in such a way that the sound absorber 12 has a volume of its cavity 12 d that is as large as possible.
  • FIG. 3 shows a perspective view of the cylinder head cover 10 comprising the nozzle 11 .
  • the cylinder head cover 10 having a circular design is connected to the cylinder head 8 , which also has a circular design, by means of a non-positive connection, in particular a screw connection, whereas, alternatively, they can also be materially interconnected, e.g., by means of a weld joint.
  • Both the cylinder head cover 10 and the cylinder head 8 can have a shape which deviates from the circular cross-sectional shape, with the cylinder head cover 10 and the cylinder head 8 preferably having the same cross-sectional shape.
  • a seal not shown in the figures e.g., an O-ring, can be arranged on the surface 10 a of the cylinder head cover 10 which faces the valve plate 5 in order to tightly connect the cylinder head cover 10 to the cylinder head 8 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
US17/757,577 2019-12-19 2020-11-12 Hermetically encapsulated refrigerant compressor Abandoned US20230031688A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ATGM50235/2019 2019-12-19
ATGM50235/2019U AT17214U1 (de) 2019-12-19 2019-12-19 Hermetisch gekapselter Kältemittelverdichter
PCT/AT2020/060401 WO2021119683A1 (de) 2019-12-19 2020-11-12 Hermetisch gekapselter kältemittelverdichter

Publications (1)

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US20230031688A1 true US20230031688A1 (en) 2023-02-02

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ID=76476455

Family Applications (1)

Application Number Title Priority Date Filing Date
US17/757,577 Abandoned US20230031688A1 (en) 2019-12-19 2020-11-12 Hermetically encapsulated refrigerant compressor

Country Status (5)

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US (1) US20230031688A1 (de)
EP (1) EP4077942B1 (de)
CN (1) CN114930022A (de)
AT (1) AT17214U1 (de)
WO (1) WO2021119683A1 (de)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4793775A (en) * 1984-10-13 1988-12-27 Aspera S.R.L. Hermetic motor-compressor unit for refrigeration circuits
US5678983A (en) * 1993-05-07 1997-10-21 Empresa Brasileira De Compressores S/A - Embraco Discharge fluid actuated assist for opening an outlet reed valve of a hermetic compressor system
US20060039808A1 (en) * 2003-05-12 2006-02-23 Masanori Kobayashi Refrigerant compressor
US20090022605A1 (en) * 2007-07-16 2009-01-22 Jung Hyoun Kim Hermetic compressor
US20090038329A1 (en) * 2005-05-03 2009-02-12 Whirlpool S.A. Suction muffler for a refrigeration compressor
US20160222954A1 (en) * 2015-02-04 2016-08-04 Lg Electronics Inc. Reciprocating compressor
US9541079B2 (en) * 2011-04-11 2017-01-10 Panasonic Intellectual Property Management Co., Ltd. Sealed compressor

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100587268C (zh) * 2004-12-22 2010-02-03 Acc奥地利有限公司 密封的致冷剂压缩机
WO2006109239A1 (en) * 2005-04-12 2006-10-19 Arcelik Anonim Sirketi A compressor
BRPI0503282A (pt) * 2005-08-01 2007-03-13 Brasil Compressores Sa compressor hermético com sistema de dissipação de calor
WO2008032507A1 (en) * 2006-09-13 2008-03-20 Panasonic Corporation Compressor
JP4946767B2 (ja) * 2007-10-03 2012-06-06 パナソニック株式会社 密閉型圧縮機
WO2009072244A1 (en) * 2007-12-06 2009-06-11 Panasonic Corporation Hermetic compressor
BRPI0803457B1 (pt) * 2008-09-05 2020-11-10 Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda arranjo de sucção para compressor hermético de refrigeração
CN202132204U (zh) * 2011-06-09 2012-02-01 杭州斯波兰冷暖设备有限公司 低噪音压缩机吸排气装置
WO2017191228A1 (en) * 2016-05-05 2017-11-09 Arcelik Anonim Sirketi A hermetic compressor with increased performance

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4793775A (en) * 1984-10-13 1988-12-27 Aspera S.R.L. Hermetic motor-compressor unit for refrigeration circuits
US5678983A (en) * 1993-05-07 1997-10-21 Empresa Brasileira De Compressores S/A - Embraco Discharge fluid actuated assist for opening an outlet reed valve of a hermetic compressor system
US20060039808A1 (en) * 2003-05-12 2006-02-23 Masanori Kobayashi Refrigerant compressor
US20090038329A1 (en) * 2005-05-03 2009-02-12 Whirlpool S.A. Suction muffler for a refrigeration compressor
US20090022605A1 (en) * 2007-07-16 2009-01-22 Jung Hyoun Kim Hermetic compressor
US9541079B2 (en) * 2011-04-11 2017-01-10 Panasonic Intellectual Property Management Co., Ltd. Sealed compressor
US20160222954A1 (en) * 2015-02-04 2016-08-04 Lg Electronics Inc. Reciprocating compressor

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Publication number Publication date
EP4077942B1 (de) 2023-09-06
CN114930022A (zh) 2022-08-19
WO2021119683A1 (de) 2021-06-24
AT17214U1 (de) 2021-09-15
EP4077942A1 (de) 2022-10-26

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