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US3864064A - Suction muffler tube for compressor - Google Patents

Suction muffler tube for compressor Download PDF

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Publication number
US3864064A
US3864064A US340553A US34055373A US3864064A US 3864064 A US3864064 A US 3864064A US 340553 A US340553 A US 340553A US 34055373 A US34055373 A US 34055373A US 3864064 A US3864064 A US 3864064A
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United States
Prior art keywords
tube
intake
compressor
muffler
housing
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.)
Expired - Lifetime
Application number
US340553A
Inventor
Edwin L Gannaway
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.)
Sundstrand Corp
Original Assignee
Sundstrand Corp
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Filing date
Publication date
Application filed by Sundstrand Corp filed Critical Sundstrand Corp
Priority to US340553A priority Critical patent/US3864064A/en
Priority to JP49016879A priority patent/JPS49120206A/ja
Priority to DE19742407650 priority patent/DE2407650A1/en
Priority to AU65767/74A priority patent/AU481578B2/en
Priority to FR7407229A priority patent/FR2228164B1/fr
Priority to IL44364A priority patent/IL44364A/en
Priority to GB1003174A priority patent/GB1448604A/en
Priority to CA194,715A priority patent/CA1023323A/en
Priority to IT49334/74A priority patent/IT1011086B/en
Application granted granted Critical
Publication of US3864064A publication Critical patent/US3864064A/en
Assigned to CANADIAN IMPERIAL BANK OF COMMERCE reassignment CANADIAN IMPERIAL BANK OF COMMERCE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: YORK INTERNATIONAL CORPORATION
Assigned to CANADIAN IMPERIAL BANK OF COMMERCE reassignment CANADIAN IMPERIAL BANK OF COMMERCE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: YORK OPERATING COMPANY, F/K/A YORK INTERNATIONAL CORPORATION A DE CORP.
Assigned to CANADIAN IMPERIAL BANK OF COMMERCE reassignment CANADIAN IMPERIAL BANK OF COMMERCE SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: YORK INTERNATIONAL CORPORATION (F/K/A YORK OPERATING COMPANY)
Anticipated expiration legal-status Critical
Assigned to CANADIAN IMPERIAL BANK OF COMMERCE reassignment CANADIAN IMPERIAL BANK OF COMMERCE RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: YORK INTERNATIONAL CORPORATION, A DE CORP.
Expired - Lifetime 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S181/00—Acoustics
    • Y10S181/403—Refrigerator compresssor muffler

Definitions

  • Inductive impedance is a direct function of the length of the suction inlet tube and an inverse function of the crosssectional area ofthe inlet tube.
  • a gas compressor that attenuates both high and low frequency noise at the intake of the compressor without causing any intake starvation.
  • suction inlet tubing assembly Firstly, there is provided an inner suction inlet tube extending from the compressor inlet to the muffler. This suction inlet tube has a cross-sectional area less than that required to feed the pump inlet and thus provides a greater inductive impedance that reduces noise in the compressor.
  • a by-pass tube Surrounding the suction inlet tube is a by-pass tube extending partway up the suction inlet tube and closed around the inlet tube at the top thereof. Apertures are provided at the top of the by-pass tube to reduce noise and also provide secondary inlet flow to the compressor intake manifold.
  • the cross-sectional area of the bypass tube i.e., the area of flow passage surrounding the suction inlet tube, is also less than prior art suction inlet tubes and thus provides a greater inductive impedance to low frequency noise generated by the intake valving.
  • the combined cross-sectional area of the suction inlet tube and the by-pass tube is the same as or greater than prior art constructions so that there is no starvation at the compressor inlet.
  • FIG. 1 is a longitudinal fragmentary section of a compressor unit according to the present invention
  • FIG. 2 is a fragmentary section illustrating the inlet valving for one of the compressor cylinder
  • a gas compressor unit 10 is illustrated consisting of a hermetic housing 12 having a cup-shaped lower housing member 14 interconnected with an upper housing member 15.
  • a compressor unit 16 having a compressor block 17 supported in the lower housing 12 by suitable springs. Carried on the top of the compressor 16 is an electric motor 18 which drives the compressor through a centrally disposed shaft 20.
  • the shaft 20, supported in bearings in the frame or block 17 drives a crank shaft 22 having cranks 23 and 24 respectively driving connecting rods 26 and 27in turn pivotally connected to pistons 30 and 31 reciprocable in cylinders 33 and 34, respectively.
  • An intake and exhaust valving and manifold unit 36 is provided for conveying gases to and from the cylinders 33 and 34.
  • the valving unit 36 includes a valving plate 38 shown more clearly in FIG. 2.
  • the valve plate 38 includes a plurality of annularly arrayed inlet passages 40 along with two arcuate outlet ports 42 and 43.
  • the inlet ports 40 are selectively opened and closed by an annular reed valve 45 shown clearly in FIG. 1.
  • reed valve 45 will bend downwardly exposing the ports 40 and permitting the intake of gas into cylinder 34.
  • Suitable outlet valving is provided on top of the valving plate 38 for selectively opening and closing the ports 42 and 43 upon the upward movement of the piston 31.
  • a similar valving arrangement is provided in plate 38 for the cylinder 33.
  • an intake manifold passage 50 For supplying gas to the inlet ports, an intake manifold passage 50 is provided having a vertically disposed intake inlet 52 which receives gases from a suction inlet tubing assembly 54.
  • the suction inlet tubing 54 communicates with an annular muffler 56, for reducing inlet noise, which is suspended in the housing by spring 57.
  • the muffler 56 has openings 60 in the lower plate thereof for the purpose of receiving inlet gas to the compressor.
  • the suction tubing assembly 54 consists of a generally vertically extending inner suction inlet tube 58 extending from the compressor intake 52 to the muffler 56.
  • a concentric by-pass tube 62 Surrounding the inner suction inlet tube 58 is a concentric by-pass tube 62 which fits within the intake opening 52 and extends upwardly to a point 63 where it is fixed to the inner suction inlet tube 58.
  • By-pass tube 62 has inlet apertures 66 and 67 (rotated from the FIG. 1 view) for the purpose of receiving additional inlet fluid and also for permitting the attenuation of inlet valving noise by emitting noise waves within the housing 12 out of phase with noise from the muffler 56 to effect high frequency noise cancellation as discussed above.
  • the by-pass tube 62 has dimples 70 in the lower end thereof for maintaining concentricity between the inner intake tube 58 and the by-pass tube 62.
  • the purpose of the separate tube 62 is to provide atte'nuat'ion for low frequency noise caused by the intake valving.
  • the low frequency noise may be attenuated by increasing the inductive impedance of the intake tubing assembly. This can be done either by increasing the length of the intake tubing, or decreasing the cross-sectional area of the intake tubing.
  • a prior art intake tube 72 is illustrated in FIG. 5 having conventional by-pass apertures 74 for receiving additional inflow by-passing muffler 75 while providing the desired high-frequency noise cancellation. lf noise attenuation were attempted in this prior art construction, shown in FIG. 5, by decreasing the cross-section of suction inlet tube 72, gas starvation at the inlet 77 would occur. The present invention obviates this problem.
  • the cross section indicated by arrow 80 of the inner tube 58 is less than the prior art suction tube 72 so that the inductive impedance of the tube 58 is increased and low frequency noise attenuation is increased.
  • the cross-section indicated at 82 of the by-pass tube 62 is alsoless than the prior artintake tube 72 so that the inductive impedance of this tube is reduced and its noise attenuation increased.
  • the combined flow areas defined by the cross-sectional areas 80 and 82 are the same as or greater than the prior art flow area defined by tube intake muffler means opening into said housing means,
  • a by-passtube leading to said intake manifold and opening into said housing means without passing into the muffler means, said by-pass tube being concentric with said intake tube and surrounding the same.
  • a gas compressor comprising:
  • said compressor mounted below and driven by said electricmotor, said compressor having inlet valving which generates noise
  • a suction inlet tube extending from the muffler means alongside the electric motor to the intake manifold
  • means for reducing the'effective cross-section of the suction inlet tube without restricting the inlet gas flow to the intake manifold including a noise reducing by-pass tube surrounding the inlet tube and.
  • said by-pass tube having a closed upper end engaging the suction inlet tube, said by-pass tube having aperture means therein permitting gas inflow and also attenuating

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

Abstract

A gas compressor having a suction muffler assembly for attenuating both high and low frequency noise produced by the inlet valving of the compressor, including an inner suction tube extending from the compressor intake to a muffler and a by-pass tube surrounding the suction tube with the by-pass tube having by-pass apertures in the upper end thereof, whereby the effective cross-sectional area of the suction intake tube may be reduced thereby attenuating low frequency noise while at the same time retaining adequate gas inflow to the compressor intake.

Description

United States Patent Gannaway SUCTION MUFFLER TUBE FOR COMPRESSOR [75] Inventor: Edwin L. Gannaway, Rockford, Ill.
[73] Assignee: Sundstrand Corporation, Rockford,
Ill.
22] Filed: Mar. 12, 1973 21 Appl. No.: 340,553
[ 1 Feb.4, 1975 Miller 181/36 R X Kilbane et a1 417/312 X Primary Examiner-Carlton R. Croyle Assistant Examiner-Richard E. Gluck Attorney, Agent, or FirmWegner, Stellman, McCord, Wiles & Wood [57] ABSTRACT [56] Refe'enc Cited Z SZJ iioii i end i iii su i iin i fe i if 1V Cr -S6C area C] n u 6 UNITED STATES PATENTS may be reduced thereby attenuating low frequency noise while at the same time retaining adequate gas pray erry e a 3,337,774 6/1968 Gannsway et a1 417/312 Inflow to the compressor Intake 3,396,907 8/1968 Valbjorn 417/312 4 Claims, Drawing Figures PMENTEDFEB SHEET 20F 2 PRIOR ART F/GIZ.
SUCTION MUFFLER TUBE FOR COMPRESSOR CROSSREFERENCE TO RELATED APPLICATION Other features of the compressor are disclosed and claimed in my copendingapplication Ser. no. 385,882 filed Aug. 6, 1973.
BACKGROUND OF THE PRESENT INVENTION In gascompressors it has been conventional to provide elongated suction inlet tubing and mufflers for the purpose of reducing intake noise produced by the compressor intake valving. To further attenuate high frequency noise it has also been suggested that by-pass apertures be provided at a point intermediate the length of the intake tube for permitting intake noise waves to passinto the housing out of phase with the intake noise from the muffler'and effecting what is termed in the art as wave cancellation.
The problem with this prior construction is that it fails to attenuate the low frequency noise also emanating from the'inlet valving. Low frequency noise is reduced by raising the inductive impedance. Inductive impedance is a direct function of the length of the suction inlet tube and an inverse function of the crosssectional area ofthe inlet tube.
It is not practical to lengthen the inlet tube because of the limitation on the overall housing size, and it is also undesirable to reduce the cross-section of the suction inlet tube since this will cause intake starvation to the compressor.
It is the primary object of the present invention to minimize the intake noise problem in prior art devices described above.
SUMMARY OF THE PRESENT INVENTION In accordance with the present invention a gas compressor is provided that attenuates both high and low frequency noise at the intake of the compressor without causing any intake starvation.
This is effected through the provision of an improved suction inlet tubing assembly. Firstly, there is provided an inner suction inlet tube extending from the compressor inlet to the muffler. This suction inlet tube has a cross-sectional area less than that required to feed the pump inlet and thus provides a greater inductive impedance that reduces noise in the compressor.
Surrounding the suction inlet tube is a by-pass tube extending partway up the suction inlet tube and closed around the inlet tube at the top thereof. Apertures are provided at the top of the by-pass tube to reduce noise and also provide secondary inlet flow to the compressor intake manifold. The cross-sectional area of the bypass tube, i.e., the area of flow passage surrounding the suction inlet tube, is also less than prior art suction inlet tubes and thus provides a greater inductive impedance to low frequency noise generated by the intake valving.
However, the combined cross-sectional area of the suction inlet tube and the by-pass tube is the same as or greater than prior art constructions so that there is no starvation at the compressor inlet.
Other objects and advantages of the present invention will appear from the following description.
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal fragmentary section ofa compressor unit according to the present invention;
FIG. 2 is a fragmentary section illustrating the inlet valving for one of the compressor cylinder;
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT Referring to the drawings, particularly FIG. I, a gas compressor unit 10 is illustrated consisting of a hermetic housing 12 having a cup-shaped lower housing member 14 interconnected with an upper housing member 15.
Within the housing 12 is a compressor unit 16 having a compressor block 17 supported in the lower housing 12 by suitable springs. Carried on the top of the compressor 16 is an electric motor 18 which drives the compressor through a centrally disposed shaft 20.
The shaft 20, supported in bearings in the frame or block 17 drives a crank shaft 22 having cranks 23 and 24 respectively driving connecting rods 26 and 27in turn pivotally connected to pistons 30 and 31 reciprocable in cylinders 33 and 34, respectively. An intake and exhaust valving and manifold unit 36 is provided for conveying gases to and from the cylinders 33 and 34. The valving unit 36 includes a valving plate 38 shown more clearly in FIG. 2. The valve plate 38 includes a plurality of annularly arrayed inlet passages 40 along with two arcuate outlet ports 42 and 43.
The inlet ports 40 are selectively opened and closed by an annular reed valve 45 shown clearly in FIG. 1.
As seen in FIG. 1, upon the suction stroke of the piston 31 the reed valve 45 will bend downwardly exposing the ports 40 and permitting the intake of gas into cylinder 34. Suitable outlet valving is provided on top of the valving plate 38 for selectively opening and closing the ports 42 and 43 upon the upward movement of the piston 31.
A similar valving arrangement is provided in plate 38 for the cylinder 33.
For supplying gas to the inlet ports, an intake manifold passage 50 is provided having a vertically disposed intake inlet 52 which receives gases from a suction inlet tubing assembly 54. The suction inlet tubing 54 communicates with an annular muffler 56, for reducing inlet noise, which is suspended in the housing by spring 57. The muffler 56 has openings 60 in the lower plate thereof for the purpose of receiving inlet gas to the compressor.
As seen more clearly in FIG. 4, the suction tubing assembly 54 consists of a generally vertically extending inner suction inlet tube 58 extending from the compressor intake 52 to the muffler 56. Surrounding the inner suction inlet tube 58 is a concentric by-pass tube 62 which fits within the intake opening 52 and extends upwardly to a point 63 where it is fixed to the inner suction inlet tube 58. By-pass tube 62 has inlet apertures 66 and 67 (rotated from the FIG. 1 view) for the purpose of receiving additional inlet fluid and also for permitting the attenuation of inlet valving noise by emitting noise waves within the housing 12 out of phase with noise from the muffler 56 to effect high frequency noise cancellation as discussed above.
The by-pass tube 62 has dimples 70 in the lower end thereof for maintaining concentricity between the inner intake tube 58 and the by-pass tube 62.
The purpose of the separate tube 62 is to provide atte'nuat'ion for low frequency noise caused by the intake valving. As discussed above, the low frequency noise may be attenuated by increasing the inductive impedance of the intake tubing assembly. This can be done either by increasing the length of the intake tubing, or decreasing the cross-sectional area of the intake tubing. A prior art intake tube 72 is illustrated in FIG. 5 having conventional by-pass apertures 74 for receiving additional inflow by-passing muffler 75 while providing the desired high-frequency noise cancellation. lf noise attenuation were attempted in this prior art construction, shown in FIG. 5, by decreasing the cross-section of suction inlet tube 72, gas starvation at the inlet 77 would occur. The present invention obviates this problem.
More specifically the cross section indicated by arrow 80 of the inner tube 58 is less than the prior art suction tube 72 so that the inductive impedance of the tube 58 is increased and low frequency noise attenuation is increased. By the same token, the cross-section indicated at 82 of the by-pass tube 62 is alsoless than the prior artintake tube 72 so that the inductive impedance of this tube is reduced and its noise attenuation increased. However, the combined flow areas defined by the cross-sectional areas 80 and 82 are the same as or greater than the prior art flow area defined by tube intake muffler means opening into said housing means,
an intake muffler tube leading from said muffler means to said intake manifold, and
a by-passtube leading to said intake manifold and opening into said housing means without passing into the muffler means, said by-pass tube being concentric with said intake tube and surrounding the same.
2. A gas compressor as defined in claim 1, wherein said by-pass tube has apertures therein for attenuating intake noise.
3. A gas compressor as defined in claim 2 wherein said intake tube and said by-pass tube each have a smaller cross-section than said intake manifold.
4. A gas compressor, comprising:
a housing,
an electric motor in saidhousing,
a reciprocating piston compressor in said housing,
mounted below and driven by said electricmotor, said compressor having inlet valving which generates noise,
an intake manifold connected to said inlet valving,
muffler means mounted above the electric motor,
a suction inlet tube extending from the muffler means alongside the electric motor to the intake manifold, and
means for reducing the'effective cross-section of the suction inlet tube without restricting the inlet gas flow to the intake manifold including a noise reducing by-pass tube surrounding the inlet tube and.
opening into the intake manifold, said by-pass tube having a closed upper end engaging the suction inlet tube, said by-pass tube having aperture means therein permitting gas inflow and also attenuating

Claims (4)

1. A gas compressor, comprising: a housing means, a compressor in said housing means having intake valving, an intake manifold leading to said intake valving, intake muffler means opening into said housing means, an intake muffler tube leading from said muffler means to said intake manifold, and a by-pass tube leading to said intake manifold and opening into said housing means without passing into the muffler means, said by-pass tube being concentric with said intake tube and surrounding the same.
2. A gas compressor as defined in claim 1, wherein said by-pass tube has apertures therein for attenuating intake noise.
3. A gas compressor as defined in claim 2 wherein said intake tube and said by-pass tube each have a smaller cross-section than said intake manifold.
4. A gas compressor, comprising: a housing, an electric motor in said housing, a reciprocating piston compressor in said housing, mounted below and driven by said electric motor, said compressor having inlet valving which generates noise, an intake manifold connected to said inlet valving, muffler means mounted above the electric motor, a suction inlet tube extending from the muffler means alongside the electric motor to the intake manifold, and means for reducing the effective cross-section of the suction inlet tube without restricting the inlet gas flow to the intake manifold including a noise reducing by-pass tube surrounding the inlet tube and opening into the intake manifold, said by-pass tube having a closed upper end engaging the suction inlet tube, said by-pass tube having aperture means therein permitting gas inflow and also attenuating noise.
US340553A 1973-03-12 1973-03-12 Suction muffler tube for compressor Expired - Lifetime US3864064A (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
US340553A US3864064A (en) 1973-03-12 1973-03-12 Suction muffler tube for compressor
JP49016879A JPS49120206A (en) 1973-03-12 1974-02-13
DE19742407650 DE2407650A1 (en) 1973-03-12 1974-02-18 INTAKE SILENCER PIPE FOR COMPRESSOR
AU65767/74A AU481578B2 (en) 1973-03-12 1974-02-19 Suction muffler tube for compressor
FR7407229A FR2228164B1 (en) 1973-03-12 1974-03-04
GB1003174A GB1448604A (en) 1973-03-12 1974-03-06 Gas compressors
IL44364A IL44364A (en) 1973-03-12 1974-03-06 Compressor muffler device
CA194,715A CA1023323A (en) 1973-03-12 1974-03-12 Suction muffler tubes for compressor
IT49334/74A IT1011086B (en) 1973-03-12 1974-03-15 COMPRESSOR SILENCER DEVICE

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US340553A US3864064A (en) 1973-03-12 1973-03-12 Suction muffler tube for compressor

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US3864064A true US3864064A (en) 1975-02-04

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US340553A Expired - Lifetime US3864064A (en) 1973-03-12 1973-03-12 Suction muffler tube for compressor

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US (1) US3864064A (en)
JP (1) JPS49120206A (en)
CA (1) CA1023323A (en)
DE (1) DE2407650A1 (en)
FR (1) FR2228164B1 (en)
GB (1) GB1448604A (en)
IL (1) IL44364A (en)
IT (1) IT1011086B (en)

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4239461A (en) * 1978-11-06 1980-12-16 Copeland Corporation Compressor induction system
EP0073469A1 (en) * 1981-08-25 1983-03-09 MATSUSHITA REIKI Co., Ltd. A sealed type motor compressor
US4477229A (en) * 1982-08-25 1984-10-16 Carrier Corporation Compressor assembly and method of attaching a suction muffler thereto
US5123816A (en) * 1991-04-02 1992-06-23 Bristol Compressors Compressor suction noise attenuator and assembly
US5164552A (en) * 1990-12-27 1992-11-17 Bristol Compressors Compressor suction noise attenuator and assembly method
US5174127A (en) * 1990-11-13 1992-12-29 Tecumseh Products Company Suction muffler tube
US5186614A (en) * 1991-11-04 1993-02-16 General Motors Corporation Variable discharge flow attenuation for compressor
US5330329A (en) * 1993-06-01 1994-07-19 Copeland Corporation Suction conduit assembly mounting
US5341654A (en) * 1993-04-16 1994-08-30 Copeland Corporation Suction gas conduit
US5733106A (en) * 1995-07-29 1998-03-31 Samsung Electronics Co., Ltd. Suction muffler for a reciprocating compressor with external holes to reduce noise attenuation
US6722467B1 (en) 2002-08-28 2004-04-20 Brunswick Corporation Noise attenuator for an air supply system of an internal combustion engine
US20040223854A1 (en) * 2000-12-01 2004-11-11 Tomell Phillip A. Reciprocating piston compressor having improved noise attenuation
EP1538334A1 (en) * 1996-06-14 2005-06-08 Matsushita Refrigeration Company Hermetic-type compressor
US20060275150A1 (en) * 2005-05-23 2006-12-07 Bitzer Kuehlmaschinenbau Gmbh Refrigerant compressor
US20080118374A1 (en) * 2006-11-20 2008-05-22 Min Cheul Yun Hermetic type compressor with suction pressure adjusting device
US20080219863A1 (en) * 2007-03-06 2008-09-11 Lg Electronics Inc. Connector for hermetic compressor and suction device of working fluid using the same
US20090257892A1 (en) * 2008-03-14 2009-10-15 Danfoss Compressors Gmbh Suction muffler for a hermetically enclosed refrigerant compressor
US20100260621A1 (en) * 2009-04-10 2010-10-14 Panasonic Corporation Hermetic compressor
WO2011015954A1 (en) * 2009-08-03 2011-02-10 Koninklijke Philips Electronics, N.V. Low restriction resonator with adjustable frequency characteristics for use in compressor nebulizer systems
US8584795B1 (en) 2012-09-04 2013-11-19 Vac-Tron Equipment, Llc Filter silencer
US9931649B2 (en) 2012-08-07 2018-04-03 Vac-Tron Equipment, Llc Rotating high pressure air and water nozzle
US10166556B2 (en) 2012-08-07 2019-01-01 Vac-Tron Equipment, Llc Pulsating high pressure air and water nozzle

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DE2951463A1 (en) * 1979-12-20 1981-07-02 Copeland Corp., Sidney, Ohio Refrigerator compressor induction conduit - has silencer to reduce noise integral with moulded plastics conduit
FR2496241A1 (en) * 1980-12-12 1982-06-18 Unite Hermetique HERMETIC REFRIGERANT COMPRESSOR
US4401418B1 (en) * 1981-04-29 1998-01-06 White Consolidated Ind Inc Muffler system for refrigeration compressor

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US2886129A (en) * 1955-05-26 1959-05-12 Coopers Mech Joints Combined gas filters and silencers
US3188975A (en) * 1963-03-25 1965-06-15 Southeastern Elevator Company Hydraulic pulsation absorption system
US3387774A (en) * 1966-11-21 1968-06-11 Copeland Refrigeration Corp Means for inhibiting noise and slugging in refrigerant compressors
US3396907A (en) * 1965-07-17 1968-08-13 Danfoss As Refrigerant compressor with sound absorbing structure
US3420052A (en) * 1967-03-08 1969-01-07 North American Rockwell Combination exhaust muffler and heater
US3736074A (en) * 1972-04-20 1973-05-29 Worthington Cei Inlet, filter and noise suppressor enclosure for compressing apparatus

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Publication number Priority date Publication date Assignee Title
US2886129A (en) * 1955-05-26 1959-05-12 Coopers Mech Joints Combined gas filters and silencers
US3188975A (en) * 1963-03-25 1965-06-15 Southeastern Elevator Company Hydraulic pulsation absorption system
US3396907A (en) * 1965-07-17 1968-08-13 Danfoss As Refrigerant compressor with sound absorbing structure
US3387774A (en) * 1966-11-21 1968-06-11 Copeland Refrigeration Corp Means for inhibiting noise and slugging in refrigerant compressors
US3420052A (en) * 1967-03-08 1969-01-07 North American Rockwell Combination exhaust muffler and heater
US3736074A (en) * 1972-04-20 1973-05-29 Worthington Cei Inlet, filter and noise suppressor enclosure for compressing apparatus

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4239461A (en) * 1978-11-06 1980-12-16 Copeland Corporation Compressor induction system
EP0073469A1 (en) * 1981-08-25 1983-03-09 MATSUSHITA REIKI Co., Ltd. A sealed type motor compressor
US4477229A (en) * 1982-08-25 1984-10-16 Carrier Corporation Compressor assembly and method of attaching a suction muffler thereto
US5174127A (en) * 1990-11-13 1992-12-29 Tecumseh Products Company Suction muffler tube
US5164552A (en) * 1990-12-27 1992-11-17 Bristol Compressors Compressor suction noise attenuator and assembly method
US5123816A (en) * 1991-04-02 1992-06-23 Bristol Compressors Compressor suction noise attenuator and assembly
US5186614A (en) * 1991-11-04 1993-02-16 General Motors Corporation Variable discharge flow attenuation for compressor
US5341654A (en) * 1993-04-16 1994-08-30 Copeland Corporation Suction gas conduit
US5330329A (en) * 1993-06-01 1994-07-19 Copeland Corporation Suction conduit assembly mounting
US5733106A (en) * 1995-07-29 1998-03-31 Samsung Electronics Co., Ltd. Suction muffler for a reciprocating compressor with external holes to reduce noise attenuation
EP1538334A1 (en) * 1996-06-14 2005-06-08 Matsushita Refrigeration Company Hermetic-type compressor
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Also Published As

Publication number Publication date
IL44364A (en) 1977-01-31
FR2228164A1 (en) 1974-11-29
AU6576774A (en) 1975-08-21
IL44364A0 (en) 1974-06-30
JPS49120206A (en) 1974-11-16
GB1448604A (en) 1976-09-08
IT1011086B (en) 1977-01-20
FR2228164B1 (en) 1978-06-02
CA1023323A (en) 1977-12-27
DE2407650A1 (en) 1974-09-19

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