EP1541868A1 - Kältemittelkompressor - Google Patents

Kältemittelkompressor Download PDF

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Publication number
EP1541868A1
EP1541868A1 EP04732026A EP04732026A EP1541868A1 EP 1541868 A1 EP1541868 A1 EP 1541868A1 EP 04732026 A EP04732026 A EP 04732026A EP 04732026 A EP04732026 A EP 04732026A EP 1541868 A1 EP1541868 A1 EP 1541868A1
Authority
EP
European Patent Office
Prior art keywords
suction
valve
cylinder
valves
pressure
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.)
Withdrawn
Application number
EP04732026A
Other languages
English (en)
French (fr)
Other versions
EP1541868A4 (de
Inventor
Masanori Kobayashi
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.)
Panasonic Holdings Corp
Original Assignee
Matsushita Electric Industrial 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 Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Publication of EP1541868A1 publication Critical patent/EP1541868A1/de
Publication of EP1541868A4 publication Critical patent/EP1541868A4/de
Withdrawn legal-status Critical Current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
    • F04B39/0005—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 adaptations of pistons
    • 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
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0088—Pulsation and noise damping means using mechanical tuned 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1066—Valve plates
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible

Definitions

  • the present invention relates to an improvement in efficiency of a hermetic compressor used in freezer-refrigerators, and the like.
  • a hermetic compressor used in freezer-refrigerators, and the like has been strongly demanded.
  • the suction efficiency is increased by, for example, providing a valve device of a compression part with two holes, and the compression efficiency is improved.
  • Such a compressor is disclosed in, for example, Japanese Patent Unexamined Publication No. H3-175174.
  • an example of a conventional hermetic compressor is described with reference to drawings.
  • FIG. 6 is a sectional view showing a conventional refrigerant compressor
  • FIG. 7 is an exploded perspective view showing a valve of a conventional refrigerant compressor.
  • an outlet port 52A that is one end of a suction tube 52 is connected.
  • Another end of the suction tube 52 is connected to a piping at the low-pressure side of a refrigerating cycle (not shown).
  • a motor 53 includes a stator 54 and a rotor 55, so as to drive a compression part 56.
  • refrigerating machine oil 57 is preserved in a bottom portion of the hermetic container 51.
  • a coil spring 58 elastically supports the motor 53 and the compression part 56.
  • the compression part 56 includes a cylinder head 61, a cylinder block 62, a valve plate 64, a suction reed valve 67, a piston 68, a connecting rod 70 and a suction muffler 30.
  • the cylinder head 61 forms a suction space 61A and a discharge space 61B.
  • the cylinder block 62 contains a cylinder 63.
  • the valve plate 64 has two suction holes 65 and two discharge holes 66.
  • the suction reed valve (hereinafter, referred to as "valve") 67 has a deformation part 67A.
  • the connecting rod 70 is linked to an eccentric part 69A of a crank shaft 69.
  • the suction muffler 30 communicates to a suction space 61A via a communicating tube 30A and to the suction hole 65 of the valve plate 64, and sucks a refrigerant gas from an inlet port 30B.
  • the motor 53 drives the compression part 56, so that the piston 68 reciprocates in the cylinder 63.
  • a low temperature and low pressure refrigerant gas returning from an external refrigerating cycle (not shown) is firstly sucked into the hermetic container 51 from the suction tube 52.
  • the refrigerant gas is further sucked from the inlet port 30B of the suction muffler 30 and passes through the suction hole 65 via the communicating tube 30A.
  • the suction stroke by flexing the deformation part 67A of the valve 67, the refrigerant gas opens the valve 67 and is led to the cylinder 63.
  • the valve 67 is closed.
  • the refrigerant gas is compressed to high temperature and high pressure, passes from the discharge hole 66 through a discharge tube (not shown) and is led to the external refrigerating cycle (not shown) so as to be used for a refrigerating operation.
  • the valve 67 is so designed as to have a natural frequency for carrying out an opening and closing operation with good timing in accordance with a low-speed operation frequency. Therefore, the compressor is capable of operation with a reduced suction loss and a high volumetric efficiency.
  • valve 67 As a solution to reduce the backflow of a refrigerant gas due to delayed closing of the valve 67, designing the valve 67 to have a high natural frequency in accordance with the high-speed operation is considered. In this case, since the spring constant of the deformation part 67A is increased, an amount of flexure is reduced, so that the suction loss is increased and accordingly the refrigerating capacity and the refrigerating efficiency are lowered.
  • the refrigerant compressor of the present invention includes a piston, a cylinder and a valve plate.
  • the valve plate is provided at an opening end of the cylinder and includes a plurality of suction holes.
  • the refrigerant compressor of the present invention further includes a plurality of suction reed valves, which is provided between the opening end of the cylinder and the valve plate, for opening and closing the plurality of suction holes, respectively.
  • At least one of the suction reed valves has a natural frequency different from that of the other reed valves. With this configuration, even when an operation frequency is changed, delayed closing of the suction reed valve and reduction in an amount of flexure are prevented.
  • FIG. 1 is a sectional view showing a refrigerant compressor in an embodiment of the preset invention.
  • FIG. 2 is a front view showing a suction reed valve.
  • FIG. 3 is a sectional view showing a cylinder head part.
  • an outlet port 2A that is one end of a suction tube 2 is connected. Another end of the suction tube 2 is connected to a piping at the low-pressure side of a refrigerating cycle (not shown).
  • a motor 3 includes a stator 4 and a rotor 5, and drives a compression part 6. Furthermore, refrigerating machine oil 7 is preserved in a bottom portion of the hermetic container 1.
  • a coil spring 8 elastically supports the motor 3 and the compression part 6.
  • the compression part 6 includes a cylinder head 101, a cylinder block 12, a valve plate 110, suction reed valves (hereinafter, referred to as "valve") 120A and 120B, a piston 18, a connecting rod 20 and a suction muffler 130.
  • the cylinder head 101 forms a suction space 101A and a discharge space 101B.
  • the cylinder block 12 contains a cylinder 13.
  • the connecting rod 20 is linked to an eccentric part 19A of a crank shaft 19.
  • the suction muffler 130 communicates to a suction space 101A via a communicating tube 130A and to suction holes 112A and 112B of the valve plate 110, and sucks a refrigerant gas from an inlet port 130B.
  • the valve plate 110 has the suction holes 112A and 112B and discharge holes (not shown).
  • the suction holes 112A and 112B are respectively inclined from opening portions 114A and 114B of the valve plate 110 at the side of the cylinder 13 to opening portions 114C and 114D of the valve plate 110 at the side of cylinder head 101 in the direction in which a distance between the suction holes is reduced.
  • the valves 120A and 120B have deformation parts 122A and 122B having different lengths each other, respectively. Since the deformation part 122A is longer than the deformation part 122B, the spring constant of the valve 120A is smaller, and the valve 120A has a lower natural frequency than that of the valve 120B.
  • valves 120A and 120B are asymmetric with respect to centerlines 124A and 124B of the deformation parts 122A and 122B. Positions of center points of the suction holes 112A and 112B correspond to points 126A and 126B of the valves 120A and 120B, respectively.
  • Seal parts 128A and 128B seal the suction holes 112A and 112B provided on the valve plate 110.
  • FIG. 4 is a graph showing a pressure in a cylinder and an amount of flexure of a reed valve in one stroke in a low-speed operation of a refrigerant compressor in an embodiment of the present invention.
  • FIG. 5 is a graph showing a pressure in a cylinder and an amount of flexure of a reed valve in one stroke in a high-speed operation of a refrigerant compressor in an embodiment of the present invention.
  • the motor 3 drives the compression part 6, so that the piston 18 reciprocates in the cylinder 13.
  • a low temperature and low pressure refrigerant gas returning from an external refrigerating cycle (not shown) is firstly sucked into the hermetic container 1 from the suction tube 2.
  • the refrigerant gas is further sucked from the inlet port 130B of the suction muffler 130 and passes through the suction holes 112A and 112B via the communicating tube 130A.
  • the suction stroke by flexing the deformation parts 122A and 122B of the valves 120A and 120B, the refrigerant gas opens the valve 120A and 120B and is led to the cylinder 13.
  • valves 120A and 120B are closed, and the refrigerant gas is compressed to high temperature and high pressure, passes from the discharge hole through a discharge tube (not shown) and is led to the external refrigerating cycle to be used for a refrigerating operation.
  • the point 140A means a point at which the gas pressure load generated by differential pressure becomes larger than a resultant force of flexure load of the valves 120A-120B and an adhesion force with the viscosity of refrigerating machine oil at the seal parts of the valves 120A-120B.
  • valves 120A and 120B are closed at a point 140B at which the pressure in the cylinder 13 exceeds the pressure in the suction space 101A of the cylinder head 101, and suction of the refrigerant gas from the suction muffler 130 is completed.
  • the valve 120A repeats opening and closing operations 150A twice at a natural frequency in primary deformation mode while flexing the deformation part 122A. Since the valve 120A is selected to have a natural frequency corresponding to a low-speed operation frequency, the valve 120A completes closing substantially with the same timing as the point 140B. Furthermore, since the spring constant of the valve 120A is small, even under conditions that the flow rate of sucked gas is slow during a low-speed operation, a suction loss due to the shortage of an amount of flexure is not increased.
  • the valve 120B has a natural frequency and a spring constant higher than those of the valve 120A, and repeats opening and closing operations 150B four times between the point 140A and the point 140B.
  • the valve 120B opens widely with a certain amount of flexure according to the circulation amount of refrigerant at the first to third opening and closing operations 150B.
  • the fourth opening and closing operation since in the compression stroke, the differential pressure between the pressure in the cylinder 13 and the pressure in the suction space 101A of the cylinder head 101 is extremely small. At this time, the refrigerant gas flows in the suction hole 112A of the valve 120A that flexes more largely.
  • valve 120B hardly flexes and it completes opening and closing operation near the point 141B.
  • the valve 120B repeats opening and closing operations 151B three times and flexes with a certain amount of flexure according to the circulation amount of refrigerant, and then completes closing with good timing.
  • the point 141A means a point at which the pressure in the cylinder 13 becomes lower than the pressure in the suction space 101A of the cylinder head 101.
  • the point 141B means a point at which the pressure in the cylinder 13 exceeds the pressure in the suction space 101A of the cylinder head 101.
  • the valve 120A opens widely in a certain amount of flexure according to the circulation amount of refrigerant at the first opening and closing operation 151A.
  • the second opening and closing operation since in a compression stroke, the differential pressure between the pressure in the cylinder 13 and the pressure in the suction space 101A of the cylinder head 101 is extremely small. Therefore, the refrigerant gas passes through the suction hole 112B of the valve 120B that flexes more largely. Consequently, the valve 120A hardly flexes and it completes the opening and closing operation near the point 141B.
  • valves 120A and 120B are asymmetric with respect to the centerlines 124A and 124B of the deformation parts 122A and 122B. Therefore, working points 126A and 126B of the gas pressure load that act on the valves 120A and 120B deviate from centerlines 124A and 124B of the flexing deformation of the valves 120A and 120B. Thus, the valves 120A and 120B start to open with torsion deformation. That is to say, torsional moment due to gas pressure load acts on the valves 120A and 120B.
  • both of the shapes of the valves 120A and 120B are asymmetric with respect to the centerlines 124A and 124B of the deformation parts 122A and 122B. However, they may be configured so that only one of the shapes is asymmetric.
  • a refrigerant gas inside the hermetic container 1 passes through the suction space 101A in a high-temperature cylinder head 101 via the suction muffler 130 and is sucked into the cylinder 13 from the suction holes 112A and 112B provided on the valve plate 110.
  • the refrigerant gas inside the cylinder 13 is in a high temperature state of about 100°C by a compression action and is discharged to a discharge space 101B of the cylinder head 101.
  • the cylinder head 101 is heated to high temperature state of about 80°C.
  • the suction space 101A in the cylinder head 101 can be configured to have a reduced volume and heat receiving area, so that the thermal transmission to the flowing refrigerant gas is reduced.
  • both of the suction holes 112A and 112B are inclined, but only one of them may be inclined.
  • the number of the valves 120A and 120B is two. However, when the number is three or more, the same effect can be obtained.
  • the natural frequency is changed by varying the lengths of the valves 120A and 120B.
  • the same effect can be obtained even when the natural frequency is changed by varying the widths or shapes of the valves 120A and 120B.
  • a refrigerant compressor of the present invention includes a piston, a cylinder and a valve plate.
  • the valve plate is provided at an opening end of the cylinder and has a plurality of suction holes.
  • the refrigerant compressor of the present invention further includes a plurality of suction reed valves provided between the opening end of the cylinder and the valve plate, and opens and closes the plurality of suction holes, respectively. At least one of the suction reed valves has a natural frequency different from that of the other reed valves.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP04732026A 2003-05-12 2004-05-10 Kältemittelkompressor Withdrawn EP1541868A4 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2003133120 2003-05-12
JP2003133120 2003-05-12
JP2004120162A JP2004360686A (ja) 2003-05-12 2004-04-15 冷媒圧縮機
JP2004120162 2004-04-15
PCT/JP2004/006578 WO2004099617A1 (ja) 2003-05-12 2004-05-10 冷媒圧縮機

Publications (2)

Publication Number Publication Date
EP1541868A1 true EP1541868A1 (de) 2005-06-15
EP1541868A4 EP1541868A4 (de) 2005-12-14

Family

ID=33436441

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04732026A Withdrawn EP1541868A4 (de) 2003-05-12 2004-05-10 Kältemittelkompressor

Country Status (5)

Country Link
US (1) US20060039808A1 (de)
EP (1) EP1541868A4 (de)
JP (1) JP2004360686A (de)
KR (1) KR20050033613A (de)
WO (1) WO2004099617A1 (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2895037A1 (fr) * 2005-12-20 2007-06-22 Tecumseh Europ S A Sa Dispositif a clapets pour compresseur de fluide et compresseur de fluide
CN104619987A (zh) * 2012-09-13 2015-05-13 艾默生环境优化技术有限公司 具有引导吸入部的压缩机组件
US11236748B2 (en) 2019-03-29 2022-02-01 Emerson Climate Technologies, Inc. Compressor having directed suction
US11248605B1 (en) 2020-07-28 2022-02-15 Emerson Climate Technologies, Inc. Compressor having shell fitting
US11619228B2 (en) 2021-01-27 2023-04-04 Emerson Climate Technologies, Inc. Compressor having directed suction
US11767838B2 (en) 2019-06-14 2023-09-26 Copeland Lp Compressor having suction fitting
WO2024101596A1 (ko) * 2022-11-09 2024-05-16 삼성전자 주식회사 압축기용 머플러

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4701789B2 (ja) * 2005-03-30 2011-06-15 パナソニック株式会社 密閉型圧縮機
JP2010127100A (ja) * 2008-11-25 2010-06-10 Daikin Ind Ltd 吐出弁及び回転式圧縮機
US8747083B2 (en) * 2010-11-16 2014-06-10 Wen San Chou Air compressor having enlarged compartment for receiving pressurized air
BRPI1101993A2 (pt) * 2011-04-28 2014-02-11 Whirlpool Sa Arranjo de válvula para compressores herméticos
BRPI1105143B1 (pt) * 2011-12-15 2021-07-27 Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda Conjunto de válvulas de sucção para compressor alternativo
AT17214U1 (de) * 2019-12-19 2021-09-15 Anhui meizhi compressor co ltd Hermetisch gekapselter Kältemittelverdichter

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09273478A (ja) * 1996-04-08 1997-10-21 Toyota Autom Loom Works Ltd ピストン式圧縮機
JPH09280168A (ja) * 1996-04-10 1997-10-28 Toyota Autom Loom Works Ltd ピストン式圧縮機
EP0845595A1 (de) * 1996-06-14 1998-06-03 Matsushita Refrigeration Company Hermetisch gekapselter kompressor
EP1054157A2 (de) * 1999-05-19 2000-11-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Einlassventil für einen Kolbenkompressor
US6206655B1 (en) * 1995-09-29 2001-03-27 Matsushita Refrigeration Company Electrically-operated sealed compressor
JP2002106466A (ja) * 2000-09-28 2002-04-10 Toyota Industries Corp ピストン式圧縮機
EP1255042A2 (de) * 2001-05-01 2002-11-06 Calsonic Kansei Corporation Einlassventil für einen Taumelscheibenverdichter

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DE4200838C2 (de) * 1992-01-15 1994-12-22 Knf Neuberger Gmbh Pumpe mit vom Fördermedium gesteuerten Ventilen
JPH09228951A (ja) * 1996-02-26 1997-09-02 Matsushita Refrig Co Ltd 圧縮機のバルブ装置
BR9900229A (pt) * 1999-01-11 2000-07-11 Stumpp & Schuele Do Brasil Ind Aperfeiçoamento em processo para fabricação de válvula de membrana para transferência de fluidos/gases em compressores herméticos e/ou semi-herméticos

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6206655B1 (en) * 1995-09-29 2001-03-27 Matsushita Refrigeration Company Electrically-operated sealed compressor
JPH09273478A (ja) * 1996-04-08 1997-10-21 Toyota Autom Loom Works Ltd ピストン式圧縮機
JPH09280168A (ja) * 1996-04-10 1997-10-28 Toyota Autom Loom Works Ltd ピストン式圧縮機
EP0845595A1 (de) * 1996-06-14 1998-06-03 Matsushita Refrigeration Company Hermetisch gekapselter kompressor
EP1054157A2 (de) * 1999-05-19 2000-11-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Einlassventil für einen Kolbenkompressor
JP2002106466A (ja) * 2000-09-28 2002-04-10 Toyota Industries Corp ピストン式圧縮機
EP1255042A2 (de) * 2001-05-01 2002-11-06 Calsonic Kansei Corporation Einlassventil für einen Taumelscheibenverdichter

Non-Patent Citations (4)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 02, 30 January 1998 (1998-01-30) -& JP 09 273478 A (TOYOTA AUTOM LOOM WORKS LTD), 21 October 1997 (1997-10-21) *
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 02, 30 January 1998 (1998-01-30) -& JP 09 280168 A (TOYOTA AUTOM LOOM WORKS LTD), 28 October 1997 (1997-10-28) *
PATENT ABSTRACTS OF JAPAN vol. 2002, no. 08, 5 August 2002 (2002-08-05) -& JP 2002 106466 A (TOYOTA INDUSTRIES CORP), 10 April 2002 (2002-04-10) *
See also references of WO2004099617A1 *

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2895037A1 (fr) * 2005-12-20 2007-06-22 Tecumseh Europ S A Sa Dispositif a clapets pour compresseur de fluide et compresseur de fluide
WO2007071665A1 (fr) * 2005-12-20 2007-06-28 Tecumseh Europe S.A. Dispositif a clapets pour compresseur de fluide et compresseur de fluide
CN104619987A (zh) * 2012-09-13 2015-05-13 艾默生环境优化技术有限公司 具有引导吸入部的压缩机组件
EP2909480A4 (de) * 2012-09-13 2016-06-29 Emerson Climate Technologies Verdichteranordnung mit gerichteter saugung
US10094600B2 (en) 2012-09-13 2018-10-09 Emerson Climate Technologies, Inc. Compressor assembly with directed suction
US10928108B2 (en) 2012-09-13 2021-02-23 Emerson Climate Technologies, Inc. Compressor assembly with directed suction
US10995974B2 (en) 2012-09-13 2021-05-04 Emerson Climate Technologies, Inc. Compressor assembly with directed suction
US11236748B2 (en) 2019-03-29 2022-02-01 Emerson Climate Technologies, Inc. Compressor having directed suction
US11767838B2 (en) 2019-06-14 2023-09-26 Copeland Lp Compressor having suction fitting
US11248605B1 (en) 2020-07-28 2022-02-15 Emerson Climate Technologies, Inc. Compressor having shell fitting
US11619228B2 (en) 2021-01-27 2023-04-04 Emerson Climate Technologies, Inc. Compressor having directed suction
WO2024101596A1 (ko) * 2022-11-09 2024-05-16 삼성전자 주식회사 압축기용 머플러

Also Published As

Publication number Publication date
WO2004099617A1 (ja) 2004-11-18
US20060039808A1 (en) 2006-02-23
JP2004360686A (ja) 2004-12-24
EP1541868A4 (de) 2005-12-14
KR20050033613A (ko) 2005-04-12

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