US3820921A - Tuned exhaust for hermetic compressor - Google Patents

Tuned exhaust for hermetic compressor Download PDF

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Publication number
US3820921A
US3820921A US00207900A US20790071A US3820921A US 3820921 A US3820921 A US 3820921A US 00207900 A US00207900 A US 00207900A US 20790071 A US20790071 A US 20790071A US 3820921 A US3820921 A US 3820921A
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United States
Prior art keywords
discharge
common
tubes
cylinders
joint
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
US00207900A
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English (en)
Inventor
P Thayer
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.)
Daikin Applied Americas Inc
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Westinghouse Electric 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 Westinghouse Electric Corp filed Critical Westinghouse Electric Corp
Priority to US00207900A priority Critical patent/US3820921A/en
Priority to CA155,318A priority patent/CA977723A/en
Priority to AU48546/72A priority patent/AU471916B2/en
Priority to GB5348272A priority patent/GB1344409A/en
Priority to DE2258083A priority patent/DE2258083A1/de
Priority to FR7244155A priority patent/FR2165477A5/fr
Priority to JP47124032A priority patent/JPS4872708A/ja
Priority to IT32814/72A priority patent/IT971787B/it
Priority to DK621572AA priority patent/DK134193B/da
Application granted granted Critical
Publication of US3820921A publication Critical patent/US3820921A/en
Priority to JP1977058843U priority patent/JPS5419526Y2/ja
Assigned to MCQUAY-PERFEX, INC., A CORP. OF MN reassignment MCQUAY-PERFEX, INC., A CORP. OF MN ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: WESTINGHOUSE ELECTRIC CORPORATION, A CORP. OF PA
Assigned to MCQUAY INC. reassignment MCQUAY INC. CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: MCQUAY-PREFEX INC.
Assigned to SNYDER GENERAL CORPORATION reassignment SNYDER GENERAL CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: MCQUAY INC.
Assigned to CITICORP INDUSTRIAL CREDIT, INC. reassignment CITICORP INDUSTRIAL CREDIT, INC. SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MCQUAY INC., A MN CORP.
Assigned to CITICORP INDUSTRIAL CREDIT INC. reassignment CITICORP INDUSTRIAL CREDIT INC. SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SNYDERGENERAL CORPORATION
Assigned to CITICORP NORTH AMERICA, INC. reassignment CITICORP NORTH AMERICA, INC. SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SNYDERGENERAL CORPORATION, A MN CORP.
Assigned to SNYDERGENERAL CORPORATION, A CORP. OF MINNESOTA, MCQUAY INC., A CORP. OF MINNESOTA reassignment SNYDERGENERAL CORPORATION, A CORP. OF MINNESOTA RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: CITICORP NORTH AMERICA, INC.
Anticipated expiration legal-status Critical
Assigned to SNYDERGENERAL CORPORATION A CORP. OF DELAWARE reassignment SNYDERGENERAL CORPORATION A CORP. OF DELAWARE RELEASE BY SECOND PARTY OF A SECURITY AGREEMENT RECORDED AT REEL 5013 FRAME 592. Assignors: CITICORP NORTH AMERICA, INC. A CORP. OF DELAWARE
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
    • F04B39/0027—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
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • 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
    • Y10S417/00—Pumps
    • Y10S417/902—Hermetically sealed motor pump unit

Definitions

  • This invention relates to a discharge arrangement for a hermetic compressor having at least two radially spaced cylinders within the compressor casing. Each cylinder is provided with a respective single discharge tube within the compressor casing. Each of the single discharge tubes is connected in a group at a common joint to a respective common discharge tube.
  • the common joints are positioned at a point relative to the dimensions of the single discharge tubes and to the radial positions of their respctive cylinders such that the discharge pulses in the common discharge lines are evenly spaced which helps to increase the compressor efficiency and also minimizes the need for a muffler.
  • the single discharge tubes are flexible in the assembled relationship and may be arranged in a side-byside relationship at the common joint to cause an aspiration effect therein, thereby increasing the volumetric efficiency of the compressor.
  • hermetic compressor units have been customary for hermetic compressor units to employ an exhaust discharge arrangement including some form of a discharge muffler at the outlet of the discharge tubing. These mufflers are needed for reduc- PRIOR ART No patents are known which disclose a hermetic compressor employing flexible discharge tubes of particular, predetermined lengths to uniformly space the cylinder exhaust discharge pulses as they pass from the cylinder discharge tubes and into a common exhaust line.
  • gasoline engines such as those found in automobiles, have employed tuned cylinder exhaust header tubes of predetermined lengths to help increase the power and overall efficiency of the engine, but, as far as known, the tuned exhaust principles of the gasoline engines have never before been applied to discharge arrangements of hermetic compressors.
  • a hermetic compressor unit having at least two radially positioned cylinders and a discharge arrangement which includes one discharge tube that is to be connected to each cylinder for the purpose of providing means for discharging the cylinder exhaust gases.
  • One main discharge line which extends through the compressor casing, is connected in common within the casing to the respective group of discharge tubes.
  • the connection means for joining each common discharge line to a respective group of discharge tubes may be a hollow joint which has a plurality of inlet openings and a single outlet opening.
  • the length of the discharge tubes are selected to be in a particular predetermined relationship with each other. The relationship is chosen so as to provide uniformly spaced cylinder discharge pulses in the common discharge line.
  • Synchronizing of the discharge pulses helps to increase compressor efficiency and to decrease the noise level which affords better vibration isolation, and at the same time, minimizes the needs for cumbersome muffler arrangements.
  • the discharge tubes are chosen to be of equal lengths.
  • unequal lengths of tubing may be chosen for the purpose of obtaining evenly spaced pulses in the common discharge line.
  • the discharge tubes are made to have a relatively small diameter and may be flexible in the assembled arrangement.
  • the discharge tubes When the discharge tubes are connected to a common discharge line, they may be aligned in a side-by-side arrangement to cause an aspiration effect within the hollow joint, whereby the pulses being discharged from one of the cylinders assist in withdrawing the gas pulses from the other cylinders into the common discharge line.
  • the result of this aspiration effect is to reduce the watt input and increase the volumetric efficiency of the compressor.
  • FIG. 1 is a fragmentaryvertical cross section of a two cylinder compressor employing the discharge arrangement of the present invention
  • FIG. 2 is a fragmentary vertical cross section of a six cylinder compressor employing the discharge arrangement of the present invention.
  • FIG. 3 shows an unfolded view of the discharge arrangement of this invention as employed in the six cylinder compressor of FIG. 2.
  • FIG. 1 shows a two cylinder, hermetic refrigerant compressor 1 of the type having an opposed cylinder arrangement and a vertical crankshaft.
  • the compressor housing 2 is gas tight and comprises an upperhalf shell 6 and lower half shell 8 welded together at seam 7.
  • Resiliently supported within the compressor housing 2 by coil springs 4 are an electric motor component 3 and a compressor component 9.
  • Radially positioned around the motor crankshaft are the cylinders 12 and 14.
  • Each cylinder 12 and 14 is provided with a single, respective discharge tube 16 and 18 of particular predetermined dimensions for enabling the cylindergases to be discharged.
  • Each single discharge tube 16 and 18 is connected together inside of easing 2 and to a common discharge line 20 by means of a tubular common joint 22.
  • Common joint 22 is positioned at a point relative to the respective dimensions of each of the single discharge tubes 16 and 18 and to the radial positions of their respective cylinders 12 and 14, as will be explained more fully hereinafter.
  • Common discharge line 20 extends through an opening 21 in the compressor casing upper half shell 6 to provide discharge means for the compressed cylinder gases.
  • Common joint 22 is hollow and is provided with a plurality of inlet openings, one opening being provided for each respective single discharge tube that is to be connected thereto.
  • Common joint 22 has a single outlet opening having a larger diameter than the diameters of the inlet openings, the outlet opening communicating with the common discharge line 20.
  • Gases that are discharged from the cylinders are in the form of pulse trains having various frequencies. It is known that certain frequencies are apt to cause a turbulent gas discharge flow which results in unwanted noise and vibration.
  • Prior art methods have employed mufflers, silencers, and sound absorbing chambers to cope with the noise and vibration problem.
  • these muffling devices may be inherently undesirable, because-they decrease the power and overall efficiency of the compressor, consume large areas of space within the compressor casing, and require the use of discharge tubing having relatively large diameters.
  • the discharge pulsations arriving at hollow joint 22 are evenly spaced and uniformly timed.
  • the lengths of the single discharge tubes are chosen such that when their respective, radially positioned cylinders are equi-angularly spaced, tubes of equal lengths and equal diameters are employed in the discharge arrangement 15. If the respective, radially positioned cylinders are not equi-angularly spaced, then single discharge tubes of equal diameters but of nonequal lengths are employed for a given direction of rotation of the compressor crankshaft.
  • the lengths must be chosen with regard to the direction of crankshaft rotation to accordingly insure that the discharge pulses from the respective cylinders are evenly spaced when received at common joint 22.
  • the diameters of single discharge tubes 16 and 18 may be reduced. Reducing the diameter of discharge tubes 16 and 18 enables them to be flexible in the assembled discharge arrangement 15, while the common discharge line 20, because of its larger diameter, remains relatively rigid. Due to the flexiblenature of tubes 16 and 18, they are adapted to be bent and aligned in a side by-side arrangement when they are to be connected to hollow joint 22. The result of aligning tubes 16 and 18 in a side-by-side relationship at their point of connection with hollow joint 22 is to thereby create an aspiration effect within the joint 22, by which gas being discharged from one of the cylinders actually helps to withdraw the discharge pulses from the opposing cylinder. As a consequence of this aspiration effect at hollow joint 22, the watt input to the compressor motor can be reduced and the volumetric efficiency of the compressor will also beincreased.
  • FIG. 2 shows a hermetic compressor having six cylinders and employing a discharge arrangement 50 of the present invention.
  • Cylinders 30, 31, 32, 33, 34, and 35 are radially arranged around the compressor crankshaft.
  • Each cylinder has a respective single discharge tube 36, 37, 38, 39, 40 and 41.
  • Single dischargetubes 30, 31, and 32 are joined together in a group and are connected to a respective common discharge line 46 inside of casing 2 by means of a tubular hollow joint 42.
  • Single discharge tubes 33, 34 and 35 are also joined together in a group and are connected to their respective common discharge line 48 inside of casing 2 by means of a tubular hollow joint 44.
  • the common discharge lines 46 and 48 extend through hermetic casing 2 in order that the cylinder gas pulses may be discharged.
  • Hollow joints 42 and 44 have three inlet openings, one to accommodate each respective discharge tube, and one outlet opening for communicating with their respective common discharge lines 46 and 48.
  • the lengths and diameters of single discharge tubes 36-41 are chosen to be equal relative to each other when cylinders30-35 are equi-angularly spaced.
  • FIG. 3 shows an unfolded view of-the six cylinder discharge arrangement 50 as illustrated in FIG. 2.
  • the diameters of discharge tubes 36-41 will again be chosen to be equal, but the lengths of the tubes 36-41 will be non-equal. Regardless of whether the cylinders are equi-angularly arranged or not, the lengths of discharge tubes 36-41 must be chosen to accordingly produce uniformly timed and evenly spaced cylinder gas discharge pulses at common joints 42 and 44 and within common discharge lines 46 and 48.
  • single discharge tubes 36-41 can be given smaller diameters than what would have normally been required had mufflers been employed.
  • the diameters of tubes 36-41 are smaller than those of the common discharge lines 46 and 48, which also enable tubes 36-41 to be relatively flexible when assembled in the discharge arrangement 50.
  • a first group of single discharge tubes 36, 37, and 38 and a second group of discharge tubes 39, 40, and 41, are each connected to their respective common discharge lines 46 and 48 by hollow joints 42 and 44.
  • Each single discharge tube group is connected to its respective joint with the discharge tubes of that group being aligned in a side-by-side arrangement. As previously described in the two cylinder arrangement of FIG.
  • this side-byside aligning of the single discharge tubes causes an as piration effect to occur at each hollow joint 42 and 44.
  • the aspiration effect results in a lower motor watt input and increased compressor volumetric efficiency.
  • the lengths of the tubes will be chosen accordingly so as to again insure that uniformly spaced discharge pulses are produced in the respective common discharge lines thereby minimizing the need of mufflers.
  • the hollow joint is to be positioned inside of the compressor casing, it is to be understood that many of the aforementioned benefits of the invention may also be obtained when the single discharge tubes extend through the casing and are joined to a common discharge line by means of the hollow joint at a point outside of compressor casing.
  • a hermetic refrigerant compressor having at least two radially positioned cylinders within the hermetic compressor casing, a single discharge tube for each cylinder, said single discharge tubes having outlet ends directed in the same flow direction and in generally parallel relation into a common discharge line at a common joint, the common joint being positioned at a point relative to the respective dimensions of each of said single discharge tubes and the radial positions of their respective cylinders so that the discharge pulses from each of said single discharge tubes into the common discharge line are evenly spaced, and each discharge pulse causes an aspirating effect upon the succeeding discharge pulses into the same common joint.
  • a refrigerant discharge line arrangement comprising:
  • a single discharge tube having an inlet end connected to each cylinder, and an outlet end;
  • a discharge line having an inlet end receiving the outlet ends of at least two of said discharge tubes at a common joint, the outlet ends of said tubes being directed in the same flow direction and in generally parallel relation into said common joint;
  • said common joint being so located relative to the lengths of said discharge tubes that the discharge pulses from each of said tubes into said joint are evenly spaced from the discharge pulses from the others of said tubes connected to said joint so that an aspirating effect is provided by each discharge pulse upon the succeeding pulses;
  • a hermetic refrigerant compressor having at least two radially positioned cylinders with at least one common discharge line extending from within the hermetic compressor casing, a single discharge tube within said casing for each cylinder, a group of said single discharge tubes having their outlet ends being gathered together and directed in the same flow direction and in generally parallel relation into a respective common discharge line at a common joint, the common joint being positioned inside the casing at a point relative to the respective dimensions of each of said single discharge tubes connected thereto and to' the radial positions of their respective cylinders that the discharge pulses from each of said single discharge tubes into the common discharge line are evenly spaced, and each discharge pulse causes an aspirating effect upon the succeeding discharge pulses into the same common oint.
  • each of said single discharge tubes is of substantially equal length and diameter and said radially positioned cylinders are equi-angularly positioned.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US00207900A 1971-12-14 1971-12-14 Tuned exhaust for hermetic compressor Expired - Lifetime US3820921A (en)

Priority Applications (10)

Application Number Priority Date Filing Date Title
US00207900A US3820921A (en) 1971-12-14 1971-12-14 Tuned exhaust for hermetic compressor
CA155,318A CA977723A (en) 1971-12-14 1972-11-01 Tuned exhaust for hermetic compressor
AU48546/72A AU471916B2 (en) 1971-12-14 1972-11-06 Improvements in or relating to hermetic compressor
GB5348272A GB1344409A (en) 1971-12-14 1972-11-20 Reciprocating compressor
DE2258083A DE2258083A1 (de) 1971-12-14 1972-11-27 Mehrzylindrischer kompressor
JP47124032A JPS4872708A (it) 1971-12-14 1972-12-12
FR7244155A FR2165477A5 (it) 1971-12-14 1972-12-12
DK621572AA DK134193B (da) 1971-12-14 1972-12-13 Hermetisk lukket kompressor.
IT32814/72A IT971787B (it) 1971-12-14 1972-12-13 Compressore ermetico
JP1977058843U JPS5419526Y2 (it) 1971-12-14 1977-05-11

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00207900A US3820921A (en) 1971-12-14 1971-12-14 Tuned exhaust for hermetic compressor

Publications (1)

Publication Number Publication Date
US3820921A true US3820921A (en) 1974-06-28

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ID=22772434

Family Applications (1)

Application Number Title Priority Date Filing Date
US00207900A Expired - Lifetime US3820921A (en) 1971-12-14 1971-12-14 Tuned exhaust for hermetic compressor

Country Status (9)

Country Link
US (1) US3820921A (it)
JP (2) JPS4872708A (it)
AU (1) AU471916B2 (it)
CA (1) CA977723A (it)
DE (1) DE2258083A1 (it)
DK (1) DK134193B (it)
FR (1) FR2165477A5 (it)
GB (1) GB1344409A (it)
IT (1) IT971787B (it)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4549859A (en) * 1983-07-12 1985-10-29 Aspera S.P.A. Suspension system for hermetic motor-compressors of refrigerators and the like
US4730994A (en) * 1986-12-12 1988-03-15 Tecumseh Products Company Compressor with improved exposed outboard thrust plate and method of assembly
US4813852A (en) * 1987-03-11 1989-03-21 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Discharge arrangement of a compressor having a plurality of compression chambers
US5236312A (en) * 1991-12-23 1993-08-17 Ford Motor Company Swash-plate-type air conditioning pump
US5762479A (en) * 1996-02-01 1998-06-09 Empresa Brasileira De Compressores S/A - Embarco Discharge arrangement for a hermetic compressor
US6692239B2 (en) * 2000-07-28 2004-02-17 Sanyo Electric Co., Ltd. Reciprocating compressor
US20080317619A1 (en) * 2007-06-22 2008-12-25 Emerson Climate Technologies, Inc. Tandem compressor system and method
US20090038684A1 (en) * 2007-08-09 2009-02-12 Optimum Power Technology L.P. Pulsation Attenuation
US20100111713A1 (en) * 2007-08-09 2010-05-06 Optimum Power Technology L.P. Apparatuses, systems, and methods for improved performance of a pressurized system
US9869497B2 (en) 2013-04-03 2018-01-16 Carrier Corporation Discharge manifold for use with multiple compressors

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1600301A (en) * 1977-02-10 1981-10-14 Copeland Corp Manufacture of refigeration motor/compressor units
JPS53130509A (en) * 1977-04-20 1978-11-14 Hitachi Ltd Totally-enclosed motor compressor
JPS61145883U (it) * 1985-03-01 1986-09-09

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3146724A (en) * 1961-11-20 1964-09-01 Armco Steel Corp Pumps with pulsation damper

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4549859A (en) * 1983-07-12 1985-10-29 Aspera S.P.A. Suspension system for hermetic motor-compressors of refrigerators and the like
US4730994A (en) * 1986-12-12 1988-03-15 Tecumseh Products Company Compressor with improved exposed outboard thrust plate and method of assembly
US4813852A (en) * 1987-03-11 1989-03-21 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Discharge arrangement of a compressor having a plurality of compression chambers
US5236312A (en) * 1991-12-23 1993-08-17 Ford Motor Company Swash-plate-type air conditioning pump
US5762479A (en) * 1996-02-01 1998-06-09 Empresa Brasileira De Compressores S/A - Embarco Discharge arrangement for a hermetic compressor
US6692239B2 (en) * 2000-07-28 2004-02-17 Sanyo Electric Co., Ltd. Reciprocating compressor
US20080317619A1 (en) * 2007-06-22 2008-12-25 Emerson Climate Technologies, Inc. Tandem compressor system and method
US8118563B2 (en) * 2007-06-22 2012-02-21 Emerson Climate Technologies, Inc. Tandem compressor system and method
US20090038684A1 (en) * 2007-08-09 2009-02-12 Optimum Power Technology L.P. Pulsation Attenuation
US20100111713A1 (en) * 2007-08-09 2010-05-06 Optimum Power Technology L.P. Apparatuses, systems, and methods for improved performance of a pressurized system
US20120325356A1 (en) * 2007-08-09 2012-12-27 Optimum Power Technology L.P. Pulsation Attenuation
US9567996B2 (en) * 2007-08-09 2017-02-14 OPTIMUM Pumping Technology, Inc. Pulsation attenuation
WO2010081148A2 (en) 2009-01-12 2010-07-15 Optimum Power Technology L.P. Apparatuses, systems, and methods for improved performance of a pressurized system
US9869497B2 (en) 2013-04-03 2018-01-16 Carrier Corporation Discharge manifold for use with multiple compressors
US10288056B2 (en) 2013-04-03 2019-05-14 Carrier Corporation Discharge gas manifold for use with multiple compressors

Also Published As

Publication number Publication date
GB1344409A (en) 1974-01-23
IT971787B (it) 1974-05-10
AU4854672A (en) 1974-05-09
CA977723A (en) 1975-11-11
JPS52157508U (it) 1977-11-30
DK134193B (da) 1976-09-27
JPS5419526Y2 (it) 1979-07-19
DK134193C (it) 1977-02-28
FR2165477A5 (it) 1973-08-03
AU471916B2 (en) 1976-05-06
DE2258083A1 (de) 1973-06-20
JPS4872708A (it) 1973-10-01

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