US3507193A - Hermetic motor compressor crankcase venting system - Google Patents

Hermetic motor compressor crankcase venting system Download PDF

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Publication number
US3507193A
US3507193A US782570A US3507193DA US3507193A US 3507193 A US3507193 A US 3507193A US 782570 A US782570 A US 782570A US 3507193D A US3507193D A US 3507193DA US 3507193 A US3507193 A US 3507193A
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United States
Prior art keywords
crankcase
compressor
oil
shell
vent
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
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US782570A
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English (en)
Inventor
Gunther T Jensen
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Trane US Inc
Original Assignee
General Electric Co
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Publication date
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Publication of US3507193A publication Critical patent/US3507193A/en
Assigned to TRANE CAC, INC., A CORP. OF DE reassignment TRANE CAC, INC., A CORP. OF DE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: GENERAL ELECTRIC COMPANY A NY CORP.
Assigned to TRANE COMPANY, THE reassignment TRANE COMPANY, THE MERGER (SEE DOCUMENT FOR DETAILS). DELAWARE, EFFECTIVE FEB. 24, 1984 Assignors: A-S CAPITAL INC. A CORP OF DE
Assigned to TRANE COMPANY, THE reassignment TRANE COMPANY, THE MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE DATE 12/29/83 SURINAME Assignors: TRANE CAC, INC.
Assigned to TRANE COMPANY, THE, A WI CORP reassignment TRANE COMPANY, THE, A WI CORP MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE DATE: 12/29/83. STATE OF INCORP. WISCONSIN Assignors: TRANE CAC, INC.
Assigned to TRANE COMPANY THE reassignment TRANE COMPANY THE MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE 12/1/83 WISCONSIN Assignors: A-S CAPITAL INC., A CORP OF DE (CHANGED TO), TRANE COMPANY THE, A CORP OF WI (INTO)
Assigned to AMERICAN STANDARD INC., A CORP OF DE reassignment AMERICAN STANDARD INC., A CORP OF DE MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE 12/28/84 DELAWARE Assignors: A-S SALEM INC., A CORP. OF DE (MERGED INTO), TRANE COMPANY, THE
Anticipated expiration legal-status Critical
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
    • F04B39/128—Crankcases
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • 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

  • a hermetic compressor comprising a hermetic shell containing a body of oil in the bottom thereof and a reciprocating compressor including a substantially closed crankcase partially immersed in the oil has a restricted drain passage interconnecting the lower portion of the crankcase with the body of oil and a restricted vent interconnecting an upper portion of the crankcase with the interior of the shell above the level of the oil.
  • the flow restrictions of the drain passage and vent are selected to prevent excessive circulation of hot gases from the crankcase to the compressor shell as well as to substantially prevent two way flow of oil between the crankcase and the oil sump during operation of the compressor.
  • Hermetic refrigerant compressors of the type with which the present invention is concerned comprise a compressor for compressing the refrigerant and a motor for driving the compressor sealed within a gas tight casing or shell.
  • the compressor com rises a compressor block including a crankcase having axially aligned bearings in the upper and lower walls thereof and at least one cylinder opening into the crankcase.
  • a vertically extending drive shaft journalled in these bearings drives a piston slidably fitted within the cylinder from a drive motor positioned above the crankcase.
  • At least the lower end portion or wall of the crankcase is immersed in a body of oil contained in a sump in the lower portion of the shell so that a suitable oil pumping means such as that described in Dubberley Patent 3,098,604 can be used to convey oil from this sump to the upper bearing and to the connecting rod bearing interconnecting the piston to the drive shaft.
  • a suitable oil pumping means such as that described in Dubberley Patent 3,098,604 can be used to convey oil from this sump to the upper bearing and to the connecting rod bearing interconnecting the piston to the drive shaft.
  • means in the form of one or more drain passages are normally provided for returning oil to the sump.
  • the crankcase is open or substantially open to the interior of the shell above the oil level with the result that the interior of the crankcase operates at substantially the same pressure as the shell.
  • the drain passage or passages in the bottom wall of the crankcase serve only to return excess lubricant to the sump and the oil level within the crankcase is the same as that in the sump under all pressure conditions.
  • the crankcase is closed so there is no communication between the crankcase and the portion of the shell above the level of the oil. As a result, the level of the oil within the crankcase is generally dependent upon the relative pressures in the crankcase and shell.
  • crankcase pressure During operation of the compressor, compressed gas from the cylinder bypassing the piston increases the pressure within the crankcase sufficiently to force oil or liquid refrigerant from the crankcase into the sump.
  • the drain passage or passages To prevent build up of crankcase pressure, the drain passage or passages have to be large enough to vent all of the bypass gases to the shell and as a result are large enough to permit a substantial alternating or pulsating flow of lubricant between the crankcase and the sump under the effect of the fluctu- 3,507,193 Patented Apr. 21, 1970 ating crankcase pressures caused by the reciprocating movement of the piston.
  • a general object of the present invention is to provide a hermetic compressor comprising a combination of vent and drain means assuring a one way flow of bypass gas from the crankcase to the compressor shell, substantially eliminating any pulsating or two way flow of oil between the crankcase and the shell and substantially preventing oil from being draWn into the crankcase as a result of a sudden increase in shell pressure.
  • Further objects of the invention are the provision of a hermetic compressor unit including a substantially closed crankcase having vent and drain means for reducing the possibility of liquid sludging in the cylinder of the compressor during start up, for producing controlled foaming of the oil for noise attenuation, and for increasing compressor capacity and reducing power consumption.
  • the illustrated compressor of the present invention comprises a hermetic casing or shell having an oil or lubricant sump in the bottom thereof and containing a vertical shaft motor-compressor unit with at least the lower crankcase portion of the compressor immersed in the oil.
  • the compressor component includes at least one cylinder opening into the crankcase and the crankcase is closed except for a restricted drain passage in the bottom wall thereof below the level of oil and a cooperating restricting vent interconnecting the upper portion of the crankcase with the shell above the level of oil.
  • vent and drain passage are such as to assure a continuous flow of refrigerant vapor and oil from the crankcase to prevent the build-up of a substantial positive crankcase pressure while at the same time limiting pulsating flow of oil and refrigerant between the shell and crankcase.
  • a hermetic compressor unit comprising a shell or casing 1 in which is resiliently supported a motor compressor unit.
  • This unit comprises a compressor block 2 defining a substantially closed crankcase 3 and a cylinder 4 opening into the crankcase.
  • the compressor block also includes upper and lower axially aligned bearings 6 and 7 in which is mounted a vertically extending shaft 8 having an eccentric bearing portion 9 between the bearings 6 and 7.
  • a connecting rod 10 connects a piston 11 to the bearing 9.
  • piston 11 reciprocates or slides back and forth in the cylinder 4 in response to the reciprocating forces provided by the eccentric bearing 9 upon rotation of the shaft 8.
  • Means for driving the compressor comprises an electric motor 14 positioned in the upper portion of the shell 1 above the compressor block 2 and having a rotor 15 attached to the shaft 8.
  • the bottom of the shell 1 defines a sump for containing a body of lubricating oil 17 used to lubricate the various bearings.
  • This body of lubricant is preferably of a suflicient depth that the lower end of the crankcase including the bearing 7 is substantially immersed in the oil and is lubricated by such immersion.
  • a centrifugal pumping arrangement (not shown) including oil passages extending upwardly through shaft 8 to these bearings as described in the aforemen- 3 tioned Dubberley Patent 3,098,604. Oil seeping from the bearings flows into the crankcase 3.
  • the compressor is designed to form part of a hermetic refrigeration system including, as diagrammatically illustrated, a condenser 21, an expansion device which may be either an expansion valve or, as shown, a capillary tube 22, and an evaporator 23 connected in closed series flow relationship.
  • a condenser 21 an expansion device which may be either an expansion valve or, as shown, a capillary tube 22, and an evaporator 23 connected in closed series flow relationship.
  • low pressure or suction gas is withdrawn from the evaporator 23 through an inlet 24 in the upper portion of the shell 1.
  • This relatively cool suction gas passes downwardly through the motor 14 and through a plurality of holes 25 into an annular suction muflier 26 formed in the upper portion of the compressor block 2.
  • the suction gas flows from the muffler 26 through one or more horizontal passages 27 into an annular cavity 28 surrounding the foreward end of the cylinder 4 and from this cavity through a plurality of suction ports 29 and a suction valve into the interior or chamber 30 of the cylinder 4.
  • Refrigerant compressed by the reciprocating piston 11 flows through a discharge mufiler 31 into a discharge line 32 which includes a plurality of loops 34 immersed in the body of oil 17 and is thereafter discharged from the compressor unit through an outlet 35 to the condenser 21.
  • the momentary pressure within the crankcase is determined primarily by two diflferent conditions.
  • the first is that the fit between the piston, piston ring, and the walls of the cylinder permits compressed gas from the compression chamber 30 to bypass the piston 11 during each compression movement thereof thereby continuously introducing high pressure gas into the crankcase.
  • the second condition is a fluctuating or pulsating change in the crankcase pressure resulting from the reciprocating movement of the piston 11 within the cylinder 4.
  • the pressure in the crankcase alternately increases and decreases proportional to the change in the effective volume thereof as determined by the displacement of the piston.
  • the compressor crankcase is provided with a combination of vent and drain means designed to provide many of the advantages of both the open and closed crankcase co1npressors while minimizing the disadvantages thereof.
  • a restricted vent passage 37 in the upper portion of the crankcase 3 interconnecting the interior of the crankcase with the interior of the shell 1 above the level of the oil in the sump and a restricted drain passage 38 in a lower wall portion of the crankcase opening into the shell below the normal level of the body of oil in the shell.
  • the vent 37 is preferably located as high as possible in a side wall of the crankcase above the cylinder and opens to the interior of the shell 1 outside the sleeve 39 supporting the motor stator above the crankcase.
  • the hole should also preferably be in the side wall so that oil in the crankcase that is being rotated around the inside of the crankcase due to rotation of the crankshaft will also be expelled out the vent passage due to centrifugal force.
  • the drain hole 38 is located as low as possible so that the maximum amount of oil can be displaced from the crankcase.
  • the lower end 40 opens below the normal oil level in the sump so that the exit noise of the oil and gas from the drain passage will be mufiled by the sump oil and also cause agitation of the sump oil to produce foaming.
  • the flow restrictions of the vent and drain passages are such that under normal compressor operating conditions, the vent 37 has a flow capacity which is insufiicient to vent all of the bypass gas from the crankcase to the shell while the drain passage 38 has a flow capacity sufficient to vent the remaining bypass gas the shell but insufficient to permit a substantial two way flow of lubricant between the sump and the crankcase as a result of the normal fluctuating pressure conditions with the crankcase.
  • vent and drain means The advantages of this combination of vent and drain means and the desired restrictions, or flow capacities thereof, will become apparent from a consideration of the operation of a compressor incorporating such means.
  • the pressures within the refrigeration system including the condenser 21, the evaporator 23 and the hermetic compressor unit tend to equalize at a pressure intermediate the operating or normal suction and condenser pressures. This equalization of pressures also take place in all of the volume within the hermetic shell 1.
  • both the shell and the crankcase are at the same intermediate pressure and the level of oil within the crankcase is the same as the sump level as illustrated in the drawing.
  • the liquid contained in the sump and the crankcase is a mixture of oil and liquid refrigerant with the oil containing some dissolved refrigerant While the shell and crankcase above the oil level contains refrigerant gas.
  • crankcase pressure the magnitude of which depends upon the displacement of the piston as compared with the overall volume of the crankcase.
  • a forward movement of the piston there is an eflective increase in the crankcase volume and hence a decrease in the crankcase pressure so that some liquid refrigerant in the crankcase or refrigerant dissolved in the oil within the crankcase vaporizes.
  • the piston is acting against this increased amount of gas with a proportional increase in crankcase pressure.
  • Some of the vapor Within the crankcase is vented through the vent 37 and some of the liquid in the lower portion of the crankcase is discharged through the drain passage 38. This process repeats until all of the liquid within the bottom of the crankcase has been discharged therefrom.
  • the flow restrictions of the vent 37 and the drain passage 38 are such that during start-up, the liquid in the crankcase is forced out slowly, for example during the first five or ten seconds of operation of the compressor. During this period, and due to the aforementioned pressure conditions within the crankcase, there is an increased load on and hence a reduction in the speed of the piston. The rate of acceleration of the compressor is thus reduced so that the liquid in the cylinder can be expelled therefrom while the compressor is operating at a relatively slow speed thereby reducing the possibility of valve failure by this liquid slugging in the cylinder.
  • the restricted drain passage 38 has the additional advantage of preventing a significant two way flow of oil between the sump and the crankcase by the fluctuating pressure conditions within the crankcase. Once a positive mean pressure difference between the crankcase and the shell is established by the flow of bypass gas into the crankcase there is no significant reverse flow of lubricant into the crankcase through the passage 38 during a decrease in the fluctuating pressure within the crankcase.
  • the combination upper and lower vent and drain passages also prevents a harmful quantity of oil from being drawn into the crankcase under a sudden rise in the shell or suction pressure. This is accomplished not only by the flow restriction provided by the drain 38 but also by the presence of the upper vent 37. Under a sudden rise in shell pressure, the vent 37 permits a reverse fiow of refrigerant vapor into the crankcase thereby more quickly equalizing the crankcase and shell pressures and again establishing a pressure relationship between the crankcase and the shell which will cause only a one-way flow of oil or gasout of the drain passage. Vent 37 also serves to equalize the crankcase and shell pressures and the oil levels during shut-down periods.
  • bypass gas flows directly to the upper portion of the shell 1 so that only a fraction of the total bypass gas affects the temperature of the suction gas within the shell and hence the compressor performance.
  • the remaining bypass gas is vented below the surface of the oil through the drain passage 38 and has the additional advantage of warming this body of oil thereby decreasing the solubility of refrigerant therein.
  • the optimum flow restrictions or flow capacities of the vent passage 37 and the drain passage 38 will depend upon a number of factors including the amount of piston blow by and the relationship between the total crankcase volume and the piston displacement volume.
  • the combined flow restriction should be suflicient to maintain a slight but positive, for example from 0.1 to 5 pounds per square inch, pressure differential between the mean crankcase pressure and the shell pressure under normal operating conditions. Preferably this pressure differential is less than 2 pounds per square inch.
  • the restrictions should provide sufiicient flow of both vapor and oil from the crankcase to prevent build-up of an excessive mean pressure difference while limiting any pulsating or alternating flow of oil and refrigerant. Such alternating flow of oil or gas. as previously described, consumes power and preheats the suction gas.
  • vent-to-drain passage flow restriction ratio of about 1:2 is presently considered to be particularly effective for most compressor displacements. With such a ratio, about /3 of the bypass gas is vented through the vent passage while the remaining /a is vented through the drain passage.
  • vent and drain passages both having a length of about one inch with the diameter of the vent being 0.086 inch and the diameter of the drain 0.111 inch.
  • the invention is, of course, not limited to these specific dimensions.
  • the length of the drain passage, and hence its length-todiameter ratio should be such that during decrease in crankcase pressure in normal compressor operation, the gas-oil interface remains within the drain passage so that oil does not flow from the sump into the crankcase.
  • a hermetic compressor comprising a hermetic shell containing a body of lubricant in the bottom thereof and a reciprocating compressor mounted within said shell and having a portion submerged in said body of lubricant;
  • said compressor comprising a substantially closed crankcase, a cylinder opening into said crankcase and a reciprocating piston in said cylinder providing a compression chamber, the fit between said piston and cylinder permitting some compressed gas in said chamber to bypass said piston and flow into said crankcase, reciprocating movement of said piston in said cylinder also effecting alternating increase and decrease in crankcase pressure;
  • vent having a flow capacity sufficient to vent only a portion of the bypass gas to said shell.
  • vent and drain passage provide fiow restrictions such that liquid refrigerant and lubricant in said crankcase are slowly discharged through said drain passage during initial startup of said compressor to thereby initially decrease the acceleration of said compressor.
  • a hermetic reciprocating compressor for a hermetic refrigeration system comprising a hermetic shell for receiving suction gas from said system and containing a body of lubricant in the bottom thereof and a reciprocating compressor mounted within said shell and having a substantially closed crankcase at least partially submerged in said body of lubricant;
  • said compressor comprising a cylinder opening into said crankcase and a reciprocating piston in said cylinder providing a compression chamber, said piston fitting loosely in said cylinder and thereby permitting some compressed gas in said chamber to bypass said piston and flow into said crankcase, reciprocating movement of said piston in said cylinder also eifecting alternating increase and decrease in crankcase pressure;
  • vent having a flow capacity insufficient to vent all of the bypass gas to said shell;
  • the relative flow capacities of said vent and said drain passages substantially preventing flow of lubricant through said drain passage to said crankcase during a decrease in said crankcase pressure by reciprocating movement of said piston.
  • vent passage has a flow capacity sufilcient to prevent substantial flow of lubricant through said drain passage into said crankcase upon a sudden increase'in shell pressure during operation of said compressor.
  • vent passage extends through an upperside wall portion of said crankcase above said cylinder and has a flow restriction approximately half of that of said drain passage.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
US782570A 1968-12-10 1968-12-10 Hermetic motor compressor crankcase venting system Expired - Lifetime US3507193A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US78257068A 1968-12-10 1968-12-10

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US3507193A true US3507193A (en) 1970-04-21

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Family Applications (1)

Application Number Title Priority Date Filing Date
US782570A Expired - Lifetime US3507193A (en) 1968-12-10 1968-12-10 Hermetic motor compressor crankcase venting system

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US (1) US3507193A (de)
DE (1) DE1961271C2 (de)
ES (1) ES374383A1 (de)
FR (1) FR2025830A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2549907A1 (fr) * 1983-07-25 1985-02-01 Copeland Corp Compresseur de refrigeration hermetique
US4518323A (en) * 1983-07-25 1985-05-21 Copeland Corporation Hermetic refrigeration compressor
US4718829A (en) * 1987-01-20 1988-01-12 American Standard Inc. Noise reduction using suction gas to foam oil
EP0260214A2 (de) * 1986-09-02 1988-03-16 Carrier Corporation Kältemittelinjection ins Öl zur Geräuschverringerung
US7097435B2 (en) * 2002-06-11 2006-08-29 Tecumseh Products Company Device for draining and recharging a hermetic compressor with oil

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4063853A (en) * 1976-05-10 1977-12-20 Carrier Corporation Noise dampening means in refrigeration motor-compressor units and method
DE3209953A1 (de) * 1981-07-02 1983-01-20 Mitsubishi Denki K.K., Tokyo Oelpumpe fuer eine hermetisch abgedichtete motor-kompressor-einheit
RU2738298C2 (ru) * 2019-04-05 2020-12-11 Федеральное государственное бюджетное образовательное учреждение высшего образования "Российский государственный университет туризма и сервиса" (ФГБОУ ВО "РГУТИС") Привод компрессора теплонасосной установки

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3008628A (en) * 1957-10-03 1961-11-14 Carrier Corp Compressor
US3066857A (en) * 1960-05-18 1962-12-04 Westinghouse Electric Corp Motor compressor unit with reduced noise transmission

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3098604A (en) * 1955-07-07 1963-07-23 Gen Electric Hermetic refrigerant compressor
US3162360A (en) * 1962-05-14 1964-12-22 Carrier Corp Compressor venting system
US3248044A (en) * 1964-09-28 1966-04-26 Lennox Ind Inc Refrigerant compressor lubrication arrangement
US3334808A (en) * 1965-10-24 1967-08-08 Lennox Ind Inc Compressor lubrication arrangement

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3008628A (en) * 1957-10-03 1961-11-14 Carrier Corp Compressor
US3066857A (en) * 1960-05-18 1962-12-04 Westinghouse Electric Corp Motor compressor unit with reduced noise transmission

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2549907A1 (fr) * 1983-07-25 1985-02-01 Copeland Corp Compresseur de refrigeration hermetique
US4518323A (en) * 1983-07-25 1985-05-21 Copeland Corporation Hermetic refrigeration compressor
EP0260214A2 (de) * 1986-09-02 1988-03-16 Carrier Corporation Kältemittelinjection ins Öl zur Geräuschverringerung
EP0260214A3 (en) * 1986-09-02 1989-10-25 Carrier Corporation Refrigerant injection into oil for sound reduction
US4718829A (en) * 1987-01-20 1988-01-12 American Standard Inc. Noise reduction using suction gas to foam oil
US7097435B2 (en) * 2002-06-11 2006-08-29 Tecumseh Products Company Device for draining and recharging a hermetic compressor with oil

Also Published As

Publication number Publication date
DE1961271A1 (de) 1970-07-09
DE1961271C2 (de) 1982-04-22
FR2025830A1 (de) 1970-09-11
ES374383A1 (es) 1972-01-01

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Effective date: 19820915

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Effective date: 19831222

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Effective date: 19841226