EP2032853A1 - Compresseur de type hermétique - Google Patents

Compresseur de type hermétique

Info

Publication number
EP2032853A1
EP2032853A1 EP07744974A EP07744974A EP2032853A1 EP 2032853 A1 EP2032853 A1 EP 2032853A1 EP 07744974 A EP07744974 A EP 07744974A EP 07744974 A EP07744974 A EP 07744974A EP 2032853 A1 EP2032853 A1 EP 2032853A1
Authority
EP
European Patent Office
Prior art keywords
suction port
opening
sealed container
cooling medium
type compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP07744974A
Other languages
German (de)
English (en)
Inventor
Kazuhiro Yokota
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 Corp
Original Assignee
Panasonic Corp
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 Panasonic Corp filed Critical Panasonic Corp
Publication of EP2032853A1 publication Critical patent/EP2032853A1/fr
Withdrawn legal-status Critical Current

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
    • F04B39/0027—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
    • 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
    • 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
    • F04B39/0072—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes characterised by assembly or mounting
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00

Definitions

  • the present invention relates to a hermetic type compressor used in a refrigerator.
  • the hermetic type compressor aimed for high efficiency includes one in which a suction port of a suction muffler faces a suction tube in proximity thereto (see e.g., patent document l).
  • Fig. 4 is a cross sectional view of a conventional hermetic type compressor disclosed in patent document 1.
  • Fig. 5 is a schematic view showing a main part seen in the shaft center direction of an opening of the conventional hermetic type compressor disclosed in patent document 1.
  • Figs. 4 and 5 electrically operated element 4 accommodated in sealed container 1 and configured by stator 2 and rotor 3, compression element 5 driven by electrically operated element 4, and suction tube 7 communicating with the inside and the outside of sealed container 1 and having opening 6 opening to the inside of sealed container 1 are arranged, where compression element 5 includes shaft 8 that rotates with rotor 3, cylinder 10 forming compression chamber 9, and suction muffler 12 forming sound deadening space 11 communicating with cylinder 10, and suction port 13 linking sound deadening space 11 and the space in sealed container 1 to communicate with each other is formed in suction muffler 12 and arranged so that the shaft center of suction port 13 and the shaft center of opening 6 coincide.
  • the operation of the hermetic type compressor configured as above will now be described.
  • stator 2 When stator 2 is conducted and shaft 8 rotates with rotor 3, the cooling medium flowing from an external refrigeration system (not shown) is once released into sealed container 1 from opening 6 via suction tube 7, passed through suction port 13, suctioned into suction muffler 12, passed through noise deadening space 11, and taken into cylinder 10.
  • an external refrigeration system not shown
  • the cooling medium in sealed container 1 rotates in the same direction as the rotation of rotor 3, and the low-temperature cooling medium released from opening 6 into sealed container 1 flows in the rotating direction of rotor 3.
  • the cooling medium taken into suction muffler 12 through suction port 13 takes in the high-temperature cooling medium in sealed container 1 at high rates, whereby the intake quantity (cooling medium circulating amount) per unit time of the cooling medium reduces and a sufficient efficiency enhancement effect cannot be obtained.
  • the present invention aims to provide a hermetic type compressor having a large cooling medium circulating amount and having high efficiency.
  • the hermetic type compressor according to the present invention has a suction port of a suction muffler offset arranged in the rotating direction of a rotor with respect to an opening of a suction tube, so that low-temperature cooling medium flows in from the upstream side with respect to the flow of the cooling medium at the front of the suction port, thereby obtaining the effect of increasing the cooling medium circulating amount by increasing the mixing rate of the low-temperature cooling medium.
  • the hermetic type compressor according to the present invention is a hermetic type compressor in which the cooling medium circulating amount is increased and thus the volumetric efficiency is increased, and therefore a hermetic type compressor having high efficiency can be provided.
  • FIG. 1 is a plan cross sectional view of a hermetic type compressor according to a first embodiment of the present invention.
  • Fig. 2 is a projection view seen from a shaft center direction of an opening of the hermetic type compressor according to the first embodiment of the present invention.
  • Fig. 3 is a relational view of the offset position of a suction port and refrigerating performance of the hermetic type compressor according to the first embodiment of the present invention.
  • Fig. 4 is a cross sectional view of a conventional hermetic type compressor.
  • Fig. 5 is a schematic view of the main part seen in the shaft center direction of an opening of the conventional hermetic type compressor.
  • FIG. 1 is a plan cross sectional view of a hermetic type compressor according to a first embodiment of the present invention.
  • Fig. 2 is a projection view seen from a shaft center direction of an opening of the hermetic type compressor according to the first embodiment of the present invention.
  • suction tube 101 is fixed to sealed container 103 at opening 102 and is opened to the inside of sealed container 103, and the other end is connected to the low pressure side of an external refrigeration system (not shown).
  • Electrically operated element 106 including stator 104 connected to an inverter control device (not shown) and rotor 105, and compression element 107 driven by electrically operated element 106 are accommodated in sealed container 103. Electrically operated element 106 is operated at a plurality of rotation numbers. Sealed container 103 is filled with cooling medium. Compression element 107 is elastically supported by a plurality of coil springs 108 and includes shaft 109 fixed to rotor 105, cylinder 111 forming compression chamber 110, and suction muffler 113 forming noise deadening space 112.
  • Suction tube 101 having one end communicating with the refrigeration system (not shown) and the other end formed with opening 102 that opens to the inside of sealed container 103 is fixed to sealed container 103.
  • Noise deadening space 112 of suction muffler 113 communicates with cylinder 111.
  • Suction port 114 communicating with noise deadening space 112 and the space inside sealed container 103 is formed on the surface of outer wall surface 115 on the sealed container side of suction muffler 113 so as to open towards the inner side of sealed container 103.
  • Suction port 114 is in the vicinity of opening 102 of suction tube 101.
  • the center of suction port 114 is arranged at a position shifted in the rotating direction side of rotor 105 with respect to the center of opening 102 when seen in the shaft center direction of opening 102 of suction tube 101 (this arrangement is hereinafter referred to as "offset arrangement").
  • Now rotor 105 rotates clockwise from the top in Fig. 2.
  • the opening area of opening 102 is larger than the opening area of suction port 114, as shown in Fig. 2.
  • Opening 102 and suction port 114 are arranged so as to at least partially overlap with each other when seen in the shaft center direction of opening 102.
  • Wall part 116 projecting towards the inner surface of sealed container 103 is arranged on the side surface in the rotating direction of rotor 105 of suction muffler 113.
  • Stator 104 of electrically operated element 106 is conducted by an inverter control board (not shown), and rotor 105 and shaft 109 rotate.
  • the pressure inside sealed container 103 lowers as the pressure inside cylinder 111 lowers during the suction stroke.
  • the cooling medium flows from the refrigeration system (not shown) into sealed container 103 through opening 102 of suction tube 101.
  • the cooling medium is suctioned into suction muffler 113 from suction port 114, passed through noise deadening space 112 and compressed in cylinder 111, and again discharged to the refrigeration system (not shown).
  • the cooling medium in sealed container 103 rotates in the same direction as the rotation of rotor 105. Furthermore, the cooling medium released into sealed container 103 from opening 102 mixes with the cooling medium in sealed container 103 while being flowed by the cooling medium in sealed container 103.
  • the lowtemperature cooling medium of opening 102 is released into sealed container 103 from the upstream of suction port 114 with respect to the flow of the cooling medium at the front of suction port 114, since suction port 114 is close to opening 102 of suction tube 101 and is offset arranged in the rotating direction side of rotor 105.
  • the low-temperature cooling medium that has flowed thereto is efficiently suctioned from suction port 114, thereby reducing the rate at which the high-temperature cooling medium in sealed container 103 is suctioned.
  • the low-temperature cooling medium is efficiently supplied to cylinder 111, and the refrigerating performance of the hermetic type compressor enhances.
  • the hermetic type compressor with high efficiency is thereby achieved by enhancing the volumetric efficiency of the hermetic type compressor.
  • Fig. 3 is a relational view of the offset position of the suction port and the refrigerating performance of the hermetic type compressor according to the first embodiment of the present invention.
  • the refrigerating performance is at a peak as the position of suction port 114 is gradually spaced apart in the counter-rotating direction side from the rotating direction side of rotor 105 with respect to opening 102 of suction tube 101 (the spaced apart position is referred to as "offset position").
  • the peak is found to be at the position spaced apart in the counter-rotating direction side of rotor 105.
  • the refrigerating performance drastically drops when the position of suction port 114 is greatly offset arranged in the rotating direction side of rotor 105 with respect to opening 102 of suction tube 101. This is because most of the lowtemperature cooling medium is flowed without being suctioned from suction port 114 when opening 102 is arranged on the downstream side with respect to the flow of the cooling medium at the front of suction port 114.
  • the refrigerating performance drops when the suction port is greatly offset arranged in the counter-rotating direction side of rotor 105.
  • the offset position of opening 102 where the refrigerating performance enhances the most does not greatly change even when the rotation number of shaft 109 by inverter control is changed.
  • the flow of cooling medium released into sealed container 103 from opening 102 depends on the flow of the cooling medium in sealed container 103. Therefore, when operating at a plurality of rotation numbers by inverter control, the flow of the cooling medium at the front of suction port 114 greatly differs at maximum rotation number operation and at minimum rotation number operation of rotor 105.
  • the speed of the cooling medium returning from the refrigerating cycle (not shown) also becomes fast because the circulating amount of cooling medium is large.
  • the flow of the cooling medium at the front of suction port 114 is slow at the time of low rotation number operation, but the speed of the cooling medium returning from the refrigerating cycle (not shown) also becomes slow because the circulating amount of cooling medium is small. Therefore, the offset position of opening 102 at which the refrigerating performance enhances the most is estimated to be substantially constant.
  • compression element 107 As compression element 107 is elastically supported by coil spring 108, compression element 107 tilts in sealed container 103 when the compressor tilts due to the influence of installation state and the like of the compressor. Thus, the relative positions of suction port 114 and opening 102 changes. Since coil spring 108 reduces the vibration of the compressor, the rigidity thereof is set low, and change in relative positions of suction port 114 and opening 102 is difficult to prevent.
  • suction port 114 is arranged at outer wall surface 115 on sealed container side of suction muffler 113 in the first embodiment.
  • opening 102 and suction port 114 are arranged so as to be partially overlapped, and the opening area of opening 102 is made larger than the opening area of suction port 114. According to such configuration, suction port 114 is prevented from being largely offset arranged in the rotating direction side of rotor 105 with respect to opening 102 of suction tube 101 even when the compressor is installed in a slightly tilted manner.
  • the low-temperature cooling medium that did not flow into suction port 114 cools outer wall surface 115 on the sealed container side of suction muffler 113, and cools the cooling medium in noise deadening space 112. Therefore, the cooling medium of low temperature is supplied to cylinder 111. In consequence, the refrigerating performance of the hermetic type compressor is stably enhanced regardless of the installing conditions.
  • wall part 116 projecting from suction muffler 113 towards the inner surface of sealed container 103 is arranged in the rotating direction side of rotor 105 of suction port 114.
  • Wall part 116 inhibits the flow of the cooling medium at the front of suction port 114, and delays the flow.
  • the cooling medium of relatively low temperature remains at the front of suction port 114, and the rise in temperature of the cooling medium released into sealed container 103 from opening 102 becomes small.
  • the cooling medium of low temperature is supplied to cylinder 111, and the refrigerating performance of the hermetic type compressor enhances.
  • the inverter is used as the electrically operated element in the present first embodiment, but an induction motor in which the rotation number of rotor 105 is constant speed may also be used. Similar effects are obtained with the induction motor by offset arranging suction port 114 with respect to opening 102 in accordance with the flow of the cooling medium at the front of suction port 114.
  • the hermetic type compressor according to the present invention has high efficiency and reliability, and is applicable to the hermetic type compressor used in air conditioner, refrigerator-freezer device, and the like.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un compresseur de type hermétique, dans lequel un orifice d'aspiration (114) est disposé décalé sur le côté du sens de rotation du rotor (105), en amont de l'orifice d'aspiration (114) par rapport à l'écoulement du milieu de refroidissement, dans la zone frontale de l'orifice d'aspiration (114) par rapport à l'ouverture (102) du tuyau d'aspiration (101), de telle sorte que le milieu de refroidissement à basse température est fourni en amont de l'orifice d'aspiration (114) par rapport à l'écoulement du milieu de refroidissement dans la zone frontale de l'orifice d'aspiration (114), le milieu de refroidissement à basse température est aspiré de manière efficace depuis l'orifice d'aspiration (114), et le milieu de refroidissement à basse température est fourni au cylindre.
EP07744974A 2006-06-23 2007-06-05 Compresseur de type hermétique Withdrawn EP2032853A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006173351 2006-06-23
PCT/JP2007/061682 WO2007148549A1 (fr) 2006-06-23 2007-06-05 Compresseur de type hermétique

Publications (1)

Publication Number Publication Date
EP2032853A1 true EP2032853A1 (fr) 2009-03-11

Family

ID=38441460

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07744974A Withdrawn EP2032853A1 (fr) 2006-06-23 2007-06-05 Compresseur de type hermétique

Country Status (6)

Country Link
US (1) US20090285701A1 (fr)
EP (1) EP2032853A1 (fr)
JP (1) JP2008542597A (fr)
KR (1) KR20080011231A (fr)
CN (1) CN101326367A (fr)
WO (1) WO2007148549A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6028211B2 (ja) 2011-10-12 2016-11-16 パナソニックＩｐマネジメント株式会社 密閉型圧縮機およびこれを備えた冷凍装置
WO2022203598A1 (fr) * 2021-03-22 2022-09-29 Panasonic Appliances Refrigeration Devices Singapore Compresseur hermétique
CN114198281B (zh) * 2021-12-14 2023-09-29 珠海凌达压缩机有限公司 一种消音结构、压缩机及空调器

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3817661A (en) * 1970-02-10 1974-06-18 Carrier Corp Cylinder head for a motor compressor unit
US4313715A (en) * 1979-12-21 1982-02-02 Tecumseh Products Company Anti-slug suction muffler for hermetic refrigeration compressor
US4370104A (en) * 1980-07-22 1983-01-25 White Consolidated Industries, Inc. Suction muffler for refrigeration compressor
US4401418B1 (en) * 1981-04-29 1998-01-06 White Consolidated Ind Inc Muffler system for refrigeration compressor
JPS6251778A (ja) * 1985-08-30 1987-03-06 Toshiba Corp 密閉形圧縮機
US5224840A (en) * 1991-03-28 1993-07-06 Tecumseh Products Company Integral suction system
BR9102288A (pt) * 1991-05-28 1993-01-05 Brasileira S A Embraco Empresa Conjunto abafador de succao para compressor hermetico
IT1260703B (it) * 1992-07-03 1996-04-22 Necchi Compressori Silenziatore per motocompressori per apparati frigoriferi
US5496156A (en) * 1994-09-22 1996-03-05 Tecumseh Products Company Suction muffler
NZ500681A (en) * 1999-10-21 2002-06-28 Fisher & Paykel Appliances Ltd A linear compressor with gas bearing passages between cylinder and cylinder lining
US6558137B2 (en) * 2000-12-01 2003-05-06 Tecumseh Products Company Reciprocating piston compressor having improved noise attenuation
KR100448548B1 (ko) * 2002-04-22 2004-09-13 삼성광주전자 주식회사 실린더 조립체 및 이를 채용한 밀폐형 압축기
JP4492032B2 (ja) * 2003-03-27 2010-06-30 パナソニック株式会社 密閉型圧縮機
KR20050059494A (ko) * 2003-12-15 2005-06-21 삼성광주전자 주식회사 밀폐형 압축기

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007148549A1 *

Also Published As

Publication number Publication date
CN101326367A (zh) 2008-12-17
JP2008542597A (ja) 2008-11-27
US20090285701A1 (en) 2009-11-19
WO2007148549A1 (fr) 2007-12-27
KR20080011231A (ko) 2008-01-31

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