US20120034114A1 - Linear compressor - Google Patents

Linear compressor Download PDF

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Publication number
US20120034114A1
US20120034114A1 US13/259,382 US201013259382A US2012034114A1 US 20120034114 A1 US20120034114 A1 US 20120034114A1 US 201013259382 A US201013259382 A US 201013259382A US 2012034114 A1 US2012034114 A1 US 2012034114A1
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US
United States
Prior art keywords
hermetic container
piston
loop pipe
cylinder
operating frequency
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
US13/259,382
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English (en)
Inventor
Hyo Jae Lee
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.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
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 LG Electronics Inc filed Critical LG Electronics Inc
Assigned to LG ELECTRONICS INC. reassignment LG ELECTRONICS INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LEE, HYO JAE
Publication of US20120034114A1 publication Critical patent/US20120034114A1/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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • 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
    • F04B39/0044—Pulsation and noise damping means with vibration damping supports
    • 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
    • F04B35/045—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 using solenoids
    • 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

Definitions

  • the present invention relates to a linear compressor which can reduce vibration through the phase shift between vibration factors.
  • a compressor is a mechanical apparatus for receiving power from a power generation apparatus, such as an electric motor, a turbine, etc. and compressing the air, refrigerant or other various operating gases to raise the pressure.
  • the compressor has been widely used in electric home appliances such as refrigerators, air conditioners, etc., and its application has been expanded to the whole industry.
  • the compressors are roughly classified into a reciprocating compressor in which a compression space for sucking and discharging an operating gas is defined between a piston and a cylinder so that the piston can be linearly reciprocated in the cylinder to compress a refrigerant, a rotary compressor in which a compression space for sucking and discharging an operating gas is defined between an eccentrically-rotated roller and a cylinder so that the roller can be eccentrically rotated along the inner wall of the cylinder to compress a refrigerant, and a scroll compressor in which a compression space for sucking and discharging an operating gas is defined between an orbiting scroll and a fixed scroll so that the orbiting scroll can be rotated along the fixed scroll to compress a refrigerant.
  • linear compressor which not only improves compression efficiency but also has a simple structure has been actively developed among the reciprocating compressors.
  • the linear compressor does not have a mechanical loss caused by motion conversion since a piston is directly connected to a driving motor which performs a linear reciprocating motion.
  • FIG. 1 is a structural diagram of vibration factors of a conventional linear compressor.
  • the conventional linear compressor includes a hermetic container 10 defining a sealed space and a main body 20 composed of a cylinder, a piston and a linear motor and compressing a refrigerant in the hermetic container 10 .
  • the main body 20 is elastically supported in the hermetic container 10 by a plurality of support springs S and a loop pipe L defining a discharge passage of the refrigerant, and the hermetic container 10 is fixed to and elastically supported on the installation surface via a mount 11 provided on its bottom surface.
  • the linear compressor Normally, in the linear compressor, a permanent magnet of the linear motor driving the piston is driven together with the piston, which increases the vibration as well as the mass of a mechanism unit performing a linear reciprocating motion.
  • the linear compressor since the linear compressor operates in a resonance state to improve compression efficiency, reducing the mass of the mechanism unit to reduce vibration may unsuitably degrade the overall efficiency of the compressor. Therefore, in the linear compressor, it is necessary to optimize the vibration transferring characteristic between the hermetic container 10 and the main body 20 so as to reduce vibration.
  • the factors having an influence on the vibration transferring characteristic include the mount 11 , the support springs S, and the loop pipe L.
  • FIG. 2 is a graph showing vibration displacements of the loop pipe employed in the conventional linear compressor.
  • the design is made such that the conventional linear compressor has a rated operating frequency of 60 Hz and that the loop pipe has a natural frequency of 70 Hz to 90 Hz which is higher than the rated operating frequency.
  • the linear motor raises the operating frequency from 0 Hz to 60 Hz upon starting.
  • the natural frequency of the loop pipe is lower than the operating frequency of the linear compressor, while the operating frequency of the linear compressor is raised to the rated operating frequency upon starting, resonance occurs when the operating frequency of the linear compressor becomes equal to the natural frequency of the loop pipe, which may lead to damage of the loop pipe. It is thus preferable that the natural frequency of the loop pipe should be set higher than the rated operating frequency of the linear compressor.
  • the main body is elastically supported in the hermetic container by the support springs and the loop pipe, and the natural frequency of the loop pipe is set higher than the rated operating frequency. While the operating frequency is raised to the rated operating frequency upon starting, the exciting force of the loop pipe increases in the same direction as the exciting force of the support springs. As a result, the exciting force of the loop pipe and the exciting force of the support springs are superimposed, which amplifies vibration transferred to the entire compressor upon starting.
  • An object of the present invention is to provide a linear compressor which can reduce vibration through the phase shift.
  • a linear compressor including: a hermetic container which defines a sealed space where a refrigerant flows in and out and which has an inlet pipe and an outlet pipe; a cylinder provided in the hermetic container and having a compression space therein; a piston linearly reciprocated in the cylinder and compressing the refrigerant of the compression space; a linear motor supplying a driving force to the piston and operating the piston at a set operating frequency; a plurality of support springs elastically supporting an assembly composed of the cylinder, the piston and the linear motor on the bottom surface of the hermetic container; and a loop pipe provided to guide the refrigerant compressed in the compression space to the outlet pipe, wherein the exciting force exerted on the hermetic container by the loop pipe has an opposite phase to the exciting force exerted on the hermetic container by the support springs.
  • the natural frequency of the loop pipe may be set equal to or lower than the rated operating frequency of the linear motor.
  • the rated operating frequency of the linear motor may be set to 60 Hz, and the natural frequency of the loop pipe may be set to 50 Hz or less.
  • a linear compressor including: a hermetic container which defines a sealed space where a refrigerant flows in and out; a cylinder provided in the hermetic container and having a compression space therein; a piston linearly reciprocated in the cylinder and compressing the refrigerant of the compression space; a linear motor supplying a driving force to the piston and operating the piston at a set operating frequency; a support spring elastically supporting an assembly composed of the cylinder, the piston and the linear motor on the bottom surface of the hermetic container; and a loop pipe provided to guide the refrigerant compressed in the compression space to the outlet pipe, wherein the rated operating frequency of the linear motor is greater than the natural frequency of the loop pipe.
  • the rated operating frequency of the linear motor may be determined in proportion to the natural frequency of the loop pipe.
  • the main body is elastically supported in the hermetic container by the support springs and the loop pipe, and the natural frequency of the loop pipe is set lower than the rated operating frequency. Since the linear compressor operates at the rated operating frequency directly upon starting by using the inverter motor, the exciting force of the loop pipe moves in the opposite direction to the exciting force of the support springs at the rated operating frequency, thereby reducing vibration transferred to the entire compressor.
  • FIG. 1 is a structural diagram of vibration factors of a conventional linear compressor.
  • FIG. 2 is a graph showing vibration displacements of a loop pipe employed in the conventional linear compressor.
  • FIG. 3 is a side-sectional view of an embodiment of a linear compressor according to the present invention.
  • FIG. 4 is a graph showing vibration displacements of a loop pipe employed in the linear compressor according to the present invention.
  • FIG. 5 is a graph showing vibration amplitudes of a hermetic container by variations of the natural frequency of the loop pipe in the linear compressor according to the present invention.
  • FIG. 3 is a side-sectional view of an embodiment of a linear compressor according to the present invention.
  • a cylinder 200 , a piston 300 , and a linear motor 400 composed of an inner stator 420 , an outer stator 440 and a permanent magnet 460 are provided in a hermetic container 110 defining a sealed space.
  • the permanent magnet 460 is linearly reciprocated between the inner stator 420 and the outer stator 440 due to a mutual electromagnetic force, the piston 300 connected to the permanent magnet 460 is linearly reciprocated together with the permanent magnet 460 .
  • the outer stator 440 is secured in the axial direction by a frame 520 and a motor cover 540 .
  • the frame 520 and the motor cover 540 are coupled to each other by means of a fastening member such as a bolt, so that the outer stator 440 is secured between the frame 520 and the motor cover 540 .
  • the frame 520 may be integrated with the cylinder 200 or may be separately manufactured and coupled to the cylinder 200 . In the embodiment shown in FIG. 3 , the frame 520 and the cylinder 200 are provided as an integral unit.
  • a supporter 320 is connected to the rear of the piston 300 . Both ends of four front main springs 800 are supported by the supporter 320 and the motor cover 540 . In addition, both ends of four rear main springs 800 are supported by the supporter 320 and a back cover 560 that is coupled to the rear of the motor cover 540 . Moreover, a suction muffler 700 is provided at the rear of the piston 300 and reduces noise when a refrigerant flows into the piston 300 .
  • the piston 300 is provided as a hollow type so that the refrigerant flowing through the suction muffler 700 can be introduced into and compressed in a compression space P defined between the cylinder 200 and the piston 300 .
  • a suction valve 610 which is provided at a front end of the piston 300 , opens the front end of the piston 300 to allow the refrigerant to flow from the piston 300 to the compression space P and closes it to prevent the refrigerant from flowing backward from the compression space P to the piston 300 .
  • the refrigerant If the refrigerant is compressed in the compression space P over a given pressure by the piston 300 , it opens a discharge valve 620 positioned at a front end of the cylinder 200 .
  • the discharge valve 620 is provided in a support cap 640 secured to one end of the cylinder 200 and is elastically supported by a spiral discharge valve spring 630 .
  • the compressed high-pressure refrigerant is discharged to a discharge cap 660 through a hole formed in the support cap 640 , discharged to the outside of the linear compressor 100 through a loop pipe L, and circulated in a refrigeration cycle.
  • the respective components of the linear compressor 100 described above are supported by a front support spring 120 and a rear support spring 140 in the assembled state and spaced apart from the bottom of the hermetic container 110 . Since the components are not in direct contact with the bottom of the hermetic container 110 , vibration generated in the respective components of the linear compressor 100 while they are compressing the refrigerant is not directly transferred to the hermetic container 110 . As a result, it is possible to reduce vibration transferred to the outside of the hermetic container 110 and noise caused by the vibration of the hermetic container 110 .
  • the linear compressor As described in connection with the prior art, it is necessary for the linear compressor to optimize the vibration transferring characteristic so as to reduce vibration and also necessary to place a limitation on the design of the loop pipe L which is a factor having an influence on compression efficiency.
  • vibration transferred to the hermetic container 110 can be considered as the sum of the exciting force of the support springs 120 and 140 and the exciting force of the loop pipe L.
  • the design is made such that the exciting force of the loop pipe L has the opposite phase to the exciting force of the support springs 120 and 140 , thus reducing vibration transferred to the entire compressor.
  • FIG. 4 is a graph showing vibration displacements of the loop pipe employed in the linear compressor according to the present invention.
  • the natural frequency f lp of the loop pipe is set lower than the rated operating frequency f so as to reduce vibration through the phase shift.
  • the loop pipe vibrates in a positive (+) direction at a frequency lower than its natural frequency f lp
  • the linear motor operates at the rated operating frequency f directly upon starting in order to prevent damage of the loop pipe. At this time, if the linear motor sweeps from 0 to the rated operating frequency f upon starting, the operating frequency becomes equal to the natural frequency f lp of the loop pipe before reaching to the rated operating frequency f, which leads to resonance damaging the loop pipe. It is thus preferable to employ an inverter motor, which operates at the rated operating frequency f directly upon starting, as the linear motor.
  • the rated operating frequency f may be set to 60 Hz so that the linear motor operates at the rated operating frequency f directly upon starting, and the natural frequency f lp of the loop pipe may be set to 50 Hz or less which is lower than the rated operating frequency f.
  • FIG. 5 is a graph showing vibration amplitudes of the hermetic container by variations of the natural frequency of the loop pipe in the linear compressor according to the present invention.
  • FIG. 5 shows an experiment result of the linear compressor according to the present invention, in which experiment the vibration transferred to the entire hermetic container was measured, setting the rated operating frequency to 60 Hz and varying the natural frequency of the loop pipe.
  • the natural frequency f lp of the loop pipe is set in a frequency domain lower than 60 Hz which is the rated operating frequency f, it reduces vibration transferred to the entire hermetic container.
  • vibration of the hermetic container increases from 13 Gal to 75 Gal.
  • a vibration variation ⁇ f of the hermetic container caused by a natural frequency variation ⁇ f lp of the loop pipe is small, it can be deemed that vibration transferred to the compressor is stable in this section.
  • the natural frequency f lp of the loop pipe varies from 50 Hz to 60 Hz, vibration of the hermetic container increases from 57 Gal to 1120 Gal.
  • the vibration variation ⁇ f of the hermetic container caused by the natural frequency variation ⁇ f lp of the loop pipe is large, it can be deemed that vibration transferred to the compressor is amplified in this section.
  • vibration of the hermetic container decreases from 1120 Gal to 452 Gal.
  • the vibration variation ⁇ f of the hermetic container caused by the natural frequency variation ⁇ f lp of the loop pipe is smaller than that in the above variation amplification section, even if the actual vibration value transferred to the hermetic container decreases, it is much larger than in the above vibration stable section.
  • the natural frequency f lp of the loop pipe varies to 70 Hz or more, vibration of the hermetic container decreases to 452 Gal or less.
  • the natural frequency f lp of the loop pipe should be set in a frequency domain of 50 Hz or less in the compressor having a rated operating frequency f of 60 Hz.
  • the natural frequency f lp of the loop pipe is determined in proportion to the rated operating frequency f, it is preferable that the natural frequency f lp of the loop pipe should be set in a frequency domain of 41.6 Hz or less in the compressor having a rated operating frequency f of 50 Hz.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US13/259,382 2009-12-08 2010-12-06 Linear compressor Abandoned US20120034114A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
KR1020090121292A KR101681322B1 (ko) 2009-12-08 2009-12-08 리니어 압축기
KR10-2009-0121292 2009-12-08
PCT/KR2010/008672 WO2011071284A2 (ko) 2009-12-08 2010-12-06 리니어 압축기

Publications (1)

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US20120034114A1 true US20120034114A1 (en) 2012-02-09

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US13/259,382 Abandoned US20120034114A1 (en) 2009-12-08 2010-12-06 Linear compressor

Country Status (5)

Country Link
US (1) US20120034114A1 (ko)
EP (1) EP2511527A4 (ko)
KR (1) KR101681322B1 (ko)
CN (1) CN102439311B (ko)
WO (1) WO2011071284A2 (ko)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150226203A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US20150226196A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US20150226199A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US20150226194A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US20150226201A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US20170191714A1 (en) * 2016-01-06 2017-07-06 Johnson Controls Technology Company Vapor compression system
US10240603B2 (en) 2014-05-22 2019-03-26 Trane International Inc. Compressor having external shell with vibration isolation and pressure balance
US11208991B2 (en) * 2018-06-29 2021-12-28 Lg Electronics Inc. Reciprocating compressor

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Publication number Priority date Publication date Assignee Title
JPH11107931A (ja) * 1997-10-02 1999-04-20 Matsushita Refrig Co Ltd 密閉型能力制御圧縮機
US20050106037A1 (en) * 2003-11-14 2005-05-19 Lg Electronics Inc. Hermetic compressor
US20050175473A1 (en) * 2004-01-06 2005-08-11 Lg Electronics Inc. Linear compressor
US20050175474A1 (en) * 2004-02-10 2005-08-11 Lg Electronics Inc. Vibration reduction structure of reciprocating compressor
US20060093497A1 (en) * 2004-11-02 2006-05-04 Lg Electronics Inc. Compressor

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KR100527176B1 (ko) * 2004-03-09 2005-11-09 삼성광주전자 주식회사 리니어 압축기
JP4851457B2 (ja) * 2004-08-30 2012-01-11 エルジー エレクトロニクス インコーポレイティド リニア圧縮機の制御装置及び制御方法
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Publication number Priority date Publication date Assignee Title
JPH11107931A (ja) * 1997-10-02 1999-04-20 Matsushita Refrig Co Ltd 密閉型能力制御圧縮機
US20050106037A1 (en) * 2003-11-14 2005-05-19 Lg Electronics Inc. Hermetic compressor
US20050175473A1 (en) * 2004-01-06 2005-08-11 Lg Electronics Inc. Linear compressor
US20050175474A1 (en) * 2004-02-10 2005-08-11 Lg Electronics Inc. Vibration reduction structure of reciprocating compressor
US20060093497A1 (en) * 2004-11-02 2006-05-04 Lg Electronics Inc. Compressor

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9429150B2 (en) * 2014-02-10 2016-08-30 Haier US Appliances Solutions, Inc. Linear compressor
US20150226203A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US20150226199A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US20150226194A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US20150226201A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US9322401B2 (en) * 2014-02-10 2016-04-26 General Electric Company Linear compressor
US20150226196A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US9506460B2 (en) * 2014-02-10 2016-11-29 Haier Us Appliance Solutions, Inc. Linear compressor
US9841012B2 (en) * 2014-02-10 2017-12-12 Haier Us Appliance Solutions, Inc. Linear compressor
US9518572B2 (en) * 2014-02-10 2016-12-13 Haier Us Appliance Solutions, Inc. Linear compressor
US10240603B2 (en) 2014-05-22 2019-03-26 Trane International Inc. Compressor having external shell with vibration isolation and pressure balance
US20170191714A1 (en) * 2016-01-06 2017-07-06 Johnson Controls Technology Company Vapor compression system
US10458687B2 (en) * 2016-01-06 2019-10-29 Johnson Controls Technology Company Vapor compression system
US11208991B2 (en) * 2018-06-29 2021-12-28 Lg Electronics Inc. Reciprocating compressor

Also Published As

Publication number Publication date
KR101681322B1 (ko) 2016-11-30
CN102439311A (zh) 2012-05-02
KR20110064610A (ko) 2011-06-15
WO2011071284A2 (ko) 2011-06-16
EP2511527A2 (en) 2012-10-17
CN102439311B (zh) 2015-10-14
WO2011071284A3 (ko) 2011-11-10
EP2511527A4 (en) 2013-06-12

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Effective date: 20110920

STCB Information on status: application discontinuation

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