US3710590A - Refrigerant cooled oil system for a rotary screw compressor - Google Patents

Refrigerant cooled oil system for a rotary screw compressor Download PDF

Info

Publication number
US3710590A
US3710590A US00163890A US3710590DA US3710590A US 3710590 A US3710590 A US 3710590A US 00163890 A US00163890 A US 00163890A US 3710590D A US3710590D A US 3710590DA US 3710590 A US3710590 A US 3710590A
Authority
US
United States
Prior art keywords
oil
compressor
refrigerant
oil cooler
condenser
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
US00163890A
Inventor
E Kocher
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.)
Copeland Industrial LP
Original Assignee
Vilter Manufacturing LLC
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 Vilter Manufacturing LLC filed Critical Vilter Manufacturing LLC
Application granted granted Critical
Publication of US3710590A publication Critical patent/US3710590A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type
    • 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
    • F25B31/002—Lubrication

Definitions

  • the lubricating oil is normally provided at a positive pressure directly to the rotors of the compressor.
  • the oil is then carried by the high pressure gaseous refrigerant to an oil separator where the oil is separated from the gaseous refrigerant prior to admission of the gaseous refrigerant to the condenser.
  • the refrigeration system of the present invention is concerned primarily with the cooling of a positive displacement rotary screw compressor.
  • the refrigerant system generally includes an oil separator, condenser, high pressure receiver, expansion valve, and an evaporator.
  • the lube oil is pumped from a sump connected to the oil separator directly into the compressor.
  • An oil cooler is provided in the lubrication line between the pump and the compressor to cool the lubricant prior to admission to the compressor.
  • the lube oil in the oil cooler is cooled by pumping high pressure liquid refrigerant into the oil cooler.
  • the liquid refrigerant evaporated in the oil cooler passes through the desuperheater coil in the oil separator and is then conducted directly back to the condenser.
  • the high pressure liquid refrigerant in the oil cooler is evaporated at condenser temperature, thus assuring that the oil cooler will not be over-cooled. Also by providing maximum cooling of the lubrication oil prior to entry into the compressor, high volumetric efficiency is achieved while maintaining the discharge gas temperature high enough to assure high efficiency of oil separation in the oil separator.
  • the compressor discharge gaseous refrigerant can never be reduced below condensing temperature and will always be in a gaseous state as it passes through the oil separator.
  • the efficiency of oil separation in the oil separator is enhanced by using a desuperheating coil to reduce gaseous refrigerant temperature.
  • FIGURE shown is a diagrammatic view of a refrigeration system for a positive displacement, rotary screw compressor with the lubricating oil cooling circuit of this invention.
  • a refrigeration system of the type contemplated herein generally includes a positive displacement, rotary screw compressor 10, a primary oil separator 12, a secondary oil separator 14, a condenser 16, a high pressure receiver 18, and an evaporator 20.
  • the system is connected in series by refrigerant conduits 22, 24, 26, 28, 30 and 32 to provide a closed circuit for the refrigerant.
  • An expansion valve 34 is normally provided in the receiver evaporator conduit 30.
  • the operation of the refrigerating system is generally well known and does not require any further explanation herein.
  • the lubricating oil circuit for the compressor 10 includes a sump 36 connected by a conduit 35 to receive oil from the primary separator 12, a pump 38 connected to the sump 36 by a conduit 42 and an oil cooler 40 connected to the pump 38 by a conduit 44.
  • the lubricating oil is drawn from the sump 36 by means of the pump 38 through the conduit 42, and pumped from the pump 38 to the oil cooler 40 through the conduit 44.
  • the now cooled oil is forced from the oil cooler 40 by the pump 38 to the compressor 10 through a conduit 46.
  • Lubricating oil is thus provided directly to the compressor 10 at a reduced temperature and at a positive pressure.
  • the lubricating oil as it enters the compressor is carried by the gaseous refrigerant in the compressor 10 to the oil separators 12 and 14.
  • liquid refrigerant is used to cool the oil cooler 40 and the oil separator 12.
  • the liquid refrigerant is pumped by means of a second pump 48 through a by-pass conduit 50 pro vided between the high pressure liquid refrigerant conduit 30 and the oil cooler 40.
  • the liquid refrigerant is partially evaporated in the oil cooler 40 as it passes in heat exchange relation with the lubricating oil in the oil cooler.
  • the refrigerant is discharged from the oil cooler 40 through oil cooler discharge conduit 51 to a desuperheating coil 52 in the oil separator 12.
  • the refrigerant discharged from the oil separator is conducted directly back to the condenser 16 through conduit 53.
  • the refrigerating system operates in a conventional manner.
  • Gaseous refrigerant discharged from the compressor 10 through conduit 22 passes through the oil separator 12, conduit 24, and oil separator 14. in a gaseous state.
  • Lubricating oil contained in the gaseous refrigerant is separated and allowed to flow to the oil sump 36 through conduit 35.
  • the high pressure gaseous refrigerant then enters the condenser 16 through conduit 26.
  • the liquid high pressure refrigerant passes from the condenser 16 through conduit 28 to the high pressure receiver 18 and through the high pressure liquid refrigerant conduit 30 and the expansion valve 34 to the evaporator 20.
  • the low pressure gaseous refrigerant from the evaporator passes through the suction line 32 back to the compressor 10.
  • the compressor is cooled by means of the lubrication oil pumped from the sump 36 by the pump 38 through conduits 42 and 44 to the oil cooler 40.
  • the cooled oil is forced under pressure through conduit 46 directly into the compressor 10 where it comes in direct contact with the gaseous refrigerant in the compressor.
  • the lubricating oil is picked up by the high pressure gaseous refrigerant and is discharged from the compressor into the discharge conduit 26.
  • the temperature of the lubricating oil is reduced by by-passing high pressure liquid refrigerant from conduit 30 through by-pass conduit 50 to the oil cooler 40.
  • the liquid refrigerant is pumped by means of the pump 44 through the oil cooler 40.
  • the refrigerant discharged from the oil cooler 40 passes through conduit 51 into the desuperheating coil 52 in the oil separator.
  • the refrigerant is substantially completely evaporated in the oil superheater coil and is then passed through conduit 53 to the condenser 16.
  • the liquid refrigerant passes through the oil cooler in heat exchange relation with the lubrication oil and through the desuperheating coil reducing oil temperature to a temperature no less than condenser temperature.
  • the present invention provides for the cooling of the lubricating oil for a screw type compressor by using liquid refrigerant. This eliminates the pollution problem incident to the use of water.
  • the oil cooler does not have to be absolutely sealed since the refrigerant will not contaminate the compressor.
  • the capacity of the compressor will remain the same because of the use of high pressure liquid refrigerant discharged from the condenser.
  • Oil separation in the oil separator is improved by including a desuperheated coil in the oil separator which is connected to the refrigerant discharge conduit from the oil cooler.
  • said circuit comprising:
  • a lubricating oil pump in said conduit for pumping oil from said compressor through said oil cooler and back to the compressor
  • liquid refrigerant bypass conduit connecting said condenser discharge liquid refrigerant to said oil cooler for passing in heat exchange relation with said lubrication oil in said oil cooler
  • said lubricating oil cooling circuit includes an oil separator connected to said compressor and a de-superheater coil in said oil segarator, said oil coolingI refri erant discharge conduit emg connected throug said e-superheater coil to said condenser.
  • a refrigeration system comprising: a positive displacement, rotary screw compressor, an oil separator connected to receive high pressure gaseous refrigerant discharged from said compressor and to separate the lubricating oil therefrom, and oil sump connected to receive the separated oil from said separator, a condenser connected to receive high pressure gaseous refrigerant from said oil separator and to condense the same to a high pressure liquid refrigerant, and an expansion valve connected to the condenser to expand the condensed refrigerant to a low pressure refrigerant, an evaporator connected to receive the low pressure refrigerant and to evaporate the same for delivery to said compressor, a lubricating oil circuit connected to supply oil at a reduced temperature directly to the compressor, said circuit including an oil pump connected to the sump to pump oil under pressure to the compressor, an oil cooler connected to receive oil from the oil pump prior to admission to the compressor, a by-pass line connected to deliver high pressure liquid refrigerant to the oil cooler and a refrigerant by-pass pump in
  • said desuperheating coil includes a refrigerant discharge conduit connected to said condenser.

Abstract

A refrigeration system including a positive displacement rotary screw compressor, a condenser, an evaporator, an oil cooler and an oil separator including a sump connected in the compressor discharge line. A pump for circulating oil from the sump through the oil cooler to the compressor and a liquid refrigerant bypass circuit including a pump for supplying liquid refrigerant under pressure in heat exchange relation with the lubricating oil in the oil cooler. The refrigerant discharged from the oil cooler is directed through a desuperheating coil in the oil separator.

Description

United States Patent 1 Kocher [451 Jan. 16, 1973 54 REFRIGERANT COOLED ()lL SYSTEM 3,270,521 9/1966 Rayner ..62/84 FOR A ROTARY SCREW 3,379,033 4/1968 Grunt ..62/84 3,408,826 11/1968 SourmcruL. .,62/47() COMPRESSOR 3,408,828 ll/l968 Sourmcraiu ..62/470 [75] lnventor: Erich J. Kocher, Milwaukee, Wis. 3,535,057 10/1970 Kodru ..418/85 3,051 2 l 71 B t [73] Asstgnee: Vrlter Manufacturing Corporation, 3 56 I 9 aumgar 62/84 Milwaukee Primary Examiner-William J. Wye 22 Filed; l 19, 1971 Attorney-James E. Nilles A refrigeration system including a positive displace- [52] US. Cl. ..62/468, 184/6.16, 418/85, mem rotary Screw compressor, a condenser an 418/88 62/84 62/470 evaporator, an oil cooler and an oil separator includ- Ill"- ..F25b a p ccnnected i the compressor discharge [58] held of Search 62/84 line. A pump for circulating oil from the sump through 62/468 418/85 88 the oil cooler to the compressor and a liquid refrigerant bypass circuit including a pump for supply- [56] References C'ted ing liquid refrigerant under pressure in heat exchange UNITED STATES PATENTS relation with the lubricating oil in the oil cooler. The refrigerant discharged from the Oll cooler is directed 2,322,874 6/1943 Nelson ..62/470 through a desuperheating coil in the oil separator. 2,846,138 8/1958 Rocklyeft.... .....62/470 3,191,854 6/1965 Lowler ..418/88 6 Claims, 1 Drawing Figure .34 Q (awn/5:!
25 i 24 flu/M1101 REFRIGERANT COOLED OIL SYSTEM FOR A ROTARY scREw COMPRESSOR BACKGROUND OF THE INVENTION In a positive displacement rotary screw compressor of the type contemplated herein, the lubricating oil is normally provided at a positive pressure directly to the rotors of the compressor. The oil is then carried by the high pressure gaseous refrigerant to an oil separator where the oil is separated from the gaseous refrigerant prior to admission of the gaseous refrigerant to the condenser. The separated oil is then pumped to an oil cooler where it is cooled by passing water in heat SUMMARY OF THE INVENTION The refrigeration system of the present invention is concerned primarily with the cooling of a positive displacement rotary screw compressor. The refrigerant system generally includes an oil separator, condenser, high pressure receiver, expansion valve, and an evaporator. The lube oil is pumped from a sump connected to the oil separator directly into the compressor. An oil cooler is provided in the lubrication line between the pump and the compressor to cool the lubricant prior to admission to the compressor. The lube oil in the oil cooler is cooled by pumping high pressure liquid refrigerant into the oil cooler. The liquid refrigerant evaporated in the oil cooler passes through the desuperheater coil in the oil separator and is then conducted directly back to the condenser.
One of the primary advantages of this system is that the high pressure liquid refrigerant in the oil cooler is evaporated at condenser temperature, thus assuring that the oil cooler will not be over-cooled. Also by providing maximum cooling of the lubrication oil prior to entry into the compressor, high volumetric efficiency is achieved while maintaining the discharge gas temperature high enough to assure high efficiency of oil separation in the oil separator. The compressor discharge gaseous refrigerant can never be reduced below condensing temperature and will always be in a gaseous state as it passes through the oil separator. The efficiency of oil separation in the oil separator is enhanced by using a desuperheating coil to reduce gaseous refrigerant temperature.
Other advantages of the present invention will become apparent from the following description when read in connection with the accompanying drawing in which: i
The single FIGURE shown is a diagrammatic view of a refrigeration system for a positive displacement, rotary screw compressor with the lubricating oil cooling circuit of this invention.
DESCRIPTION OF THE INVENTION A refrigeration system of the type contemplated herein generally includes a positive displacement, rotary screw compressor 10, a primary oil separator 12, a secondary oil separator 14, a condenser 16, a high pressure receiver 18, and an evaporator 20. The system is connected in series by refrigerant conduits 22, 24, 26, 28, 30 and 32 to provide a closed circuit for the refrigerant. An expansion valve 34 is normally provided in the receiver evaporator conduit 30. The operation of the refrigerating system is generally well known and does not require any further explanation herein.
The lubricating oil circuit for the compressor 10 includes a sump 36 connected by a conduit 35 to receive oil from the primary separator 12, a pump 38 connected to the sump 36 by a conduit 42 and an oil cooler 40 connected to the pump 38 by a conduit 44. The lubricating oil is drawn from the sump 36 by means of the pump 38 through the conduit 42, and pumped from the pump 38 to the oil cooler 40 through the conduit 44. The now cooled oil is forced from the oil cooler 40 by the pump 38 to the compressor 10 through a conduit 46. Lubricating oil is thus provided directly to the compressor 10 at a reduced temperature and at a positive pressure. The lubricating oil as it enters the compressor is carried by the gaseous refrigerant in the compressor 10 to the oil separators 12 and 14.
In accordance with the invention, liquid refrigerant is used to cool the oil cooler 40 and the oil separator 12. In this regard the liquid refrigerant is pumped by means of a second pump 48 through a by-pass conduit 50 pro vided between the high pressure liquid refrigerant conduit 30 and the oil cooler 40. The liquid refrigerant is partially evaporated in the oil cooler 40 as it passes in heat exchange relation with the lubricating oil in the oil cooler. The refrigerant is discharged from the oil cooler 40 through oil cooler discharge conduit 51 to a desuperheating coil 52 in the oil separator 12. The refrigerant discharged from the oil separator is conducted directly back to the condenser 16 through conduit 53. The high pressure liquid refrigerant which is pumped through the oil cooler 40 and desuperheating coil 52 is evaporated at all times at a temperature no less than condenser temperature, thus excessive cooling of lubricating oil is prevented. It should be noted that in the event of a leak occurring in the oil cooler 40, no adverse effect will result since any refrigerant that is picked up by the lubricating oil is carried into the compressor and is separated from the oil when it passes through the oil separator.
In operation, the refrigerating system operates in a conventional manner. Gaseous refrigerant discharged from the compressor 10 through conduit 22 passes through the oil separator 12, conduit 24, and oil separator 14. in a gaseous state. Lubricating oil contained in the gaseous refrigerant is separated and allowed to flow to the oil sump 36 through conduit 35. The high pressure gaseous refrigerant then enters the condenser 16 through conduit 26.
The liquid high pressure refrigerant passes from the condenser 16 through conduit 28 to the high pressure receiver 18 and through the high pressure liquid refrigerant conduit 30 and the expansion valve 34 to the evaporator 20. The low pressure gaseous refrigerant from the evaporator passes through the suction line 32 back to the compressor 10.
The compressor is cooled by means of the lubrication oil pumped from the sump 36 by the pump 38 through conduits 42 and 44 to the oil cooler 40. The cooled oil is forced under pressure through conduit 46 directly into the compressor 10 where it comes in direct contact with the gaseous refrigerant in the compressor. The lubricating oil is picked up by the high pressure gaseous refrigerant and is discharged from the compressor into the discharge conduit 26.
The temperature of the lubricating oil is reduced by by-passing high pressure liquid refrigerant from conduit 30 through by-pass conduit 50 to the oil cooler 40. The liquid refrigerant is pumped by means of the pump 44 through the oil cooler 40. The refrigerant discharged from the oil cooler 40 passes through conduit 51 into the desuperheating coil 52 in the oil separator. The refrigerant is substantially completely evaporated in the oil superheater coil and is then passed through conduit 53 to the condenser 16. The liquid refrigerant passes through the oil cooler in heat exchange relation with the lubrication oil and through the desuperheating coil reducing oil temperature to a temperature no less than condenser temperature.
RESUME The present invention provides for the cooling of the lubricating oil for a screw type compressor by using liquid refrigerant. This eliminates the pollution problem incident to the use of water. The oil cooler does not have to be absolutely sealed since the refrigerant will not contaminate the compressor. The capacity of the compressor will remain the same because of the use of high pressure liquid refrigerant discharged from the condenser. Oil separation in the oil separator is improved by including a desuperheated coil in the oil separator which is connected to the refrigerant discharge conduit from the oil cooler.
Iclaim:
1. In a refrigeration system including a rotary screw compressor,
a condenser and an evaporator connected in series,
a lubricating oil cooling circuit for cooling and lubricating oil for said compressor,
said circuit comprising:
an oil cooler,
a lubricating oil conduit connecting said oil cooler to said compressor,
a lubricating oil pump in said conduit for pumping oil from said compressor through said oil cooler and back to the compressor,
a liquid refrigerant bypass conduit connecting said condenser discharge liquid refrigerant to said oil cooler for passing in heat exchange relation with said lubrication oil in said oil cooler,
an oil cooler refrigerant discharge conduit connecting said oil cooler to said condenser,
and a liquid refrigerant pump in said bypass conduit for pumping liquid refrigerant through said bypass conduit to said oil cooler.
2. The system according to claim 1 wherein said lubricating oil cooling circuit includes an oil separator connected to said compressor and a de-superheater coil in said oil segarator, said oil coolingI refri erant discharge conduit emg connected throug said e-superheater coil to said condenser.
3. A refrigeration system comprising: a positive displacement, rotary screw compressor, an oil separator connected to receive high pressure gaseous refrigerant discharged from said compressor and to separate the lubricating oil therefrom, and oil sump connected to receive the separated oil from said separator, a condenser connected to receive high pressure gaseous refrigerant from said oil separator and to condense the same to a high pressure liquid refrigerant, and an expansion valve connected to the condenser to expand the condensed refrigerant to a low pressure refrigerant, an evaporator connected to receive the low pressure refrigerant and to evaporate the same for delivery to said compressor, a lubricating oil circuit connected to supply oil at a reduced temperature directly to the compressor, said circuit including an oil pump connected to the sump to pump oil under pressure to the compressor, an oil cooler connected to receive oil from the oil pump prior to admission to the compressor, a by-pass line connected to deliver high pressure liquid refrigerant to the oil cooler and a refrigerant by-pass pump in said by-pass line to pump liquid refrigerant through said oil cooler in heat exchange relation with said oil.
4. The system according to claim 1 including a desuperheating coil in said oil separator, and said oil cooler including a refrigerant discharge conduit connected to said desuperheating coil.
5. The system according to claim 1 wherein said oil cooler includes a refrigerant discharge conduit connected to said condenser.
6. The system according to claim 4 wherein said desuperheating coil includes a refrigerant discharge conduit connected to said condenser.

Claims (6)

1. In a refrigeration system including a rotary screw compressor, a condenser and an evaporator connected in series, a lubricating oil cooling circuit for cooling and lubricating oil for said compressor, said circuit comprising: an oil cooler, a lubricating oil conduit connecting said oil cooler to said compressor, a lubricating oil pump in said conduit for pumping oil from said compressor through said oil cooler and back to the compressor, a liquid refrigerant bypass conduit connecting said condenser discharge liquid refrigerant to said oil cooler for passing in heat exchange relation with said lubrication oil in said oil cooler, an oil cooler refrigerant discharge conduit connecting said oil cooler to said condenser, and a liquid refrigerant pump in said bypass conduit for pumping liquid refrigerant through said bypass conduit to said oil cooler.
2. The system according to claim 1 wherein said lubricating oil cooling circuit includes an oil separator connected to said compressor and a de-superheater coil in said oil separator, said oil cooling refrigerant discharge conduit being connected through said de-superheater coil to said condenser.
3. A refrigeration system comprising: a positive displacement, rotary screw compressor, an oil separator connected to receive high pressure gaseous refrigerant discharged from said compressor and to separate the lubricating oil therefrom, and oil sump connected to receive the separated oil from said separator, a condenser connected to receive high pressure gaseous refrigerant from said oil separator and to condense the same to a high pressure liquid refrigerant, and an expansion valve connected to the condenser to expand the condensed refrigerant to a low pressure refrigerant, an evaporator connected to receive the low pressure refrigerant and to evaporate the same for delivery to said compressor, a lubricating oil circuit connected to supply oil at a reduced temperature directly to the compressor, said circuit including an oil pump connected to the sump to pump oil under pressure to the compressor, an oil cooler connected to receive oil from the oil pump prior to admission to the compressor, a by-pass line connected to deliver high pressure liquid refrigerant to the oil cooler and a refrigerAnt by-pass pump in said by-pass line to pump liquid refrigerant through said oil cooler in heat exchange relation with said oil.
4. The system according to claim 1 including a desuperheating coil in said oil separator, and said oil cooler including a refrigerant discharge conduit connected to said desuperheating coil.
5. The system according to claim 1 wherein said oil cooler includes a refrigerant discharge conduit connected to said condenser.
6. The system according to claim 4 wherein said desuperheating coil includes a refrigerant discharge conduit connected to said condenser.
US00163890A 1971-07-19 1971-07-19 Refrigerant cooled oil system for a rotary screw compressor Expired - Lifetime US3710590A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US16389071A 1971-07-19 1971-07-19

Publications (1)

Publication Number Publication Date
US3710590A true US3710590A (en) 1973-01-16

Family

ID=22592030

Family Applications (1)

Application Number Title Priority Date Filing Date
US00163890A Expired - Lifetime US3710590A (en) 1971-07-19 1971-07-19 Refrigerant cooled oil system for a rotary screw compressor

Country Status (1)

Country Link
US (1) US3710590A (en)

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3850009A (en) * 1972-02-22 1974-11-26 Sabroe T & Co Ak Cleaning of pressurized condensable gas
US3874192A (en) * 1973-03-08 1975-04-01 Maekawa Seisakusho Kk Oil cooling apparatus for refrigerators
JPS5048539A (en) * 1973-06-20 1975-04-30
US3945219A (en) * 1970-08-25 1976-03-23 Kabushiki Kaisha Maekawa Seisakusho Method of and apparatus for preventing overheating of electrical motors for compressors
US3945216A (en) * 1973-06-18 1976-03-23 Svenska Rotor Maskiner Aktiebolag Refrigeration systems
US4254637A (en) * 1979-10-19 1981-03-10 Vilter Manufacturing Corporation Refrigeration system with refrigerant cooling of compressor and its oil
US4275570A (en) * 1980-06-16 1981-06-30 Vilter Manufacturing Corporation Oil cooling means for refrigeration screw compressor
US4569640A (en) * 1982-05-13 1986-02-11 Bernard Zimmern Device for high pressure compression
US4573324A (en) * 1985-03-04 1986-03-04 American Standard Inc. Compressor motor housing as an economizer and motor cooler in a refrigeration system
US4780061A (en) * 1987-08-06 1988-10-25 American Standard Inc. Screw compressor with integral oil cooling
US5214928A (en) * 1991-04-02 1993-06-01 Omega Enterprises, Inc. Refrigeration apparatus and methods
US5433590A (en) * 1991-07-11 1995-07-18 Bitzer Kuhlmaschinenbau Gmbh & Co.Kg Cooling device for the lubrication circuit of a compressor
US5477695A (en) * 1994-01-14 1995-12-26 Thermo King Corporation Methods and apparatus for operating a refrigeration system characterized by controlling engine coolant
US5590539A (en) * 1993-11-26 1997-01-07 Omega Enterprises Inc. Refrigeration apparatus and methods
US5603222A (en) * 1995-06-09 1997-02-18 Dube; Serge Cooling method and system for a compressor of a refrigerating system
US5613368A (en) * 1991-04-02 1997-03-25 Omega Enterprises, Inc. Refrigeration apparatus and methods
WO2001011294A1 (en) * 1999-08-06 2001-02-15 American Standard Inc. Thermosiphonic oil cooler for refrigeration chiller
US20040050081A1 (en) * 2002-09-17 2004-03-18 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd) Screw refrigerating apparatus
US20100307173A1 (en) * 2009-05-15 2010-12-09 Weihua Guo Compressor and oil-cooling system
CN102252463A (en) * 2011-05-27 2011-11-23 武汉新世界制冷工业有限公司 Screw chiller for underground air conditioner
US20140216103A1 (en) * 2013-02-05 2014-08-07 Emerson Climate Technologies, Inc. Compressor cooling system
US20150007596A1 (en) * 2011-12-23 2015-01-08 Schneider Electric It Corporation Systems and methods for computer room air conditioning
CN104676934A (en) * 2015-03-10 2015-06-03 南京冷德节能科技有限公司 Double-stage falling film screw rod cold water/heat pump unit
CN109442780A (en) * 2018-09-19 2019-03-08 广州市凌静制冷设备有限公司 A kind of flooded screw water cooling unit group

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2322874A (en) * 1941-11-21 1943-06-29 Chrysler Corp Compressor oil cooling system
US2846138A (en) * 1954-12-16 1958-08-05 Acton Mfg Company Inc Refrigeration compressor
US3191854A (en) * 1960-06-02 1965-06-29 Atlas Copco Ab Compressor units
US3270521A (en) * 1965-09-08 1966-09-06 Worthington Corp Refrigerant cooled oil cooler system
US3379033A (en) * 1966-08-10 1968-04-23 Vilter Manufacturing Corp Refrigeration system and apparatus
US3408828A (en) * 1967-09-08 1968-11-05 Dunham Bush Inc Refrigeration system and system for separating oil from compressed gas
US3408826A (en) * 1967-01-27 1968-11-05 Dunham Bush Inc Refrigeration system and systems for cooling and controlling compressors
US3535057A (en) * 1968-09-06 1970-10-20 Esper Kodra Screw compressor
US3563051A (en) * 1968-08-13 1971-02-16 Thermomeccanica Italiana Apparatus for lubricating the compressor of a refrigerating installation

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2322874A (en) * 1941-11-21 1943-06-29 Chrysler Corp Compressor oil cooling system
US2846138A (en) * 1954-12-16 1958-08-05 Acton Mfg Company Inc Refrigeration compressor
US3191854A (en) * 1960-06-02 1965-06-29 Atlas Copco Ab Compressor units
US3270521A (en) * 1965-09-08 1966-09-06 Worthington Corp Refrigerant cooled oil cooler system
US3379033A (en) * 1966-08-10 1968-04-23 Vilter Manufacturing Corp Refrigeration system and apparatus
US3408826A (en) * 1967-01-27 1968-11-05 Dunham Bush Inc Refrigeration system and systems for cooling and controlling compressors
US3408828A (en) * 1967-09-08 1968-11-05 Dunham Bush Inc Refrigeration system and system for separating oil from compressed gas
US3563051A (en) * 1968-08-13 1971-02-16 Thermomeccanica Italiana Apparatus for lubricating the compressor of a refrigerating installation
US3535057A (en) * 1968-09-06 1970-10-20 Esper Kodra Screw compressor

Cited By (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3945219A (en) * 1970-08-25 1976-03-23 Kabushiki Kaisha Maekawa Seisakusho Method of and apparatus for preventing overheating of electrical motors for compressors
US3850009A (en) * 1972-02-22 1974-11-26 Sabroe T & Co Ak Cleaning of pressurized condensable gas
US3874192A (en) * 1973-03-08 1975-04-01 Maekawa Seisakusho Kk Oil cooling apparatus for refrigerators
US3945216A (en) * 1973-06-18 1976-03-23 Svenska Rotor Maskiner Aktiebolag Refrigeration systems
JPS5048539A (en) * 1973-06-20 1975-04-30
US4254637A (en) * 1979-10-19 1981-03-10 Vilter Manufacturing Corporation Refrigeration system with refrigerant cooling of compressor and its oil
US4275570A (en) * 1980-06-16 1981-06-30 Vilter Manufacturing Corporation Oil cooling means for refrigeration screw compressor
US4569640A (en) * 1982-05-13 1986-02-11 Bernard Zimmern Device for high pressure compression
US4573324A (en) * 1985-03-04 1986-03-04 American Standard Inc. Compressor motor housing as an economizer and motor cooler in a refrigeration system
US4780061A (en) * 1987-08-06 1988-10-25 American Standard Inc. Screw compressor with integral oil cooling
US5214928A (en) * 1991-04-02 1993-06-01 Omega Enterprises, Inc. Refrigeration apparatus and methods
US5613368A (en) * 1991-04-02 1997-03-25 Omega Enterprises, Inc. Refrigeration apparatus and methods
US5433590A (en) * 1991-07-11 1995-07-18 Bitzer Kuhlmaschinenbau Gmbh & Co.Kg Cooling device for the lubrication circuit of a compressor
US5590539A (en) * 1993-11-26 1997-01-07 Omega Enterprises Inc. Refrigeration apparatus and methods
US5477695A (en) * 1994-01-14 1995-12-26 Thermo King Corporation Methods and apparatus for operating a refrigeration system characterized by controlling engine coolant
US5603222A (en) * 1995-06-09 1997-02-18 Dube; Serge Cooling method and system for a compressor of a refrigerating system
WO2001011294A1 (en) * 1999-08-06 2001-02-15 American Standard Inc. Thermosiphonic oil cooler for refrigeration chiller
US20040050081A1 (en) * 2002-09-17 2004-03-18 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd) Screw refrigerating apparatus
US6755039B2 (en) * 2002-09-17 2004-06-29 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Screw refrigerating apparatus
US9316227B2 (en) 2009-05-15 2016-04-19 Emerson Climate Technologies, Inc. Compressor and oil-cooling system
US20100307173A1 (en) * 2009-05-15 2010-12-09 Weihua Guo Compressor and oil-cooling system
US8590324B2 (en) * 2009-05-15 2013-11-26 Emerson Climate Technologies, Inc. Compressor and oil-cooling system
CN102252463A (en) * 2011-05-27 2011-11-23 武汉新世界制冷工业有限公司 Screw chiller for underground air conditioner
US9845977B2 (en) * 2011-12-23 2017-12-19 Schneider Electric It Corporation Systems and methods for computer room air conditioning
US20150007596A1 (en) * 2011-12-23 2015-01-08 Schneider Electric It Corporation Systems and methods for computer room air conditioning
AU2011383984B2 (en) * 2011-12-23 2017-09-07 Schneider Electric It Corporation Systems and methods for computer room air conditioning
US9562709B2 (en) * 2013-02-05 2017-02-07 Emerson Climate Technologies, Inc. Compressor cooling system
US20140216103A1 (en) * 2013-02-05 2014-08-07 Emerson Climate Technologies, Inc. Compressor cooling system
US10047987B2 (en) 2013-02-05 2018-08-14 Emerson Climate Technologies, Inc. Compressor cooling system
US10539351B2 (en) 2013-02-05 2020-01-21 Emerson Climate Technologies, Inc. Compressor with fluid cavity for cooling
US10746443B2 (en) 2013-02-05 2020-08-18 Emerson Climate Technologies, Inc. Compressor cooling system
US11371497B2 (en) 2013-02-05 2022-06-28 Emerson Climate Technologies, Inc. Compressor with fluid cavity for cooling
CN104676934A (en) * 2015-03-10 2015-06-03 南京冷德节能科技有限公司 Double-stage falling film screw rod cold water/heat pump unit
CN104676934B (en) * 2015-03-10 2017-04-12 南京冷德节能科技有限公司 Double-stage falling film screw rod cold water/heat pump unit
CN109442780A (en) * 2018-09-19 2019-03-08 广州市凌静制冷设备有限公司 A kind of flooded screw water cooling unit group

Similar Documents

Publication Publication Date Title
US3710590A (en) Refrigerant cooled oil system for a rotary screw compressor
US6058727A (en) Refrigeration system with integrated oil cooling heat exchanger
US5899091A (en) Refrigeration system with integrated economizer/oil cooler
JPH10132395A (en) Turbo refrigerator
GB2446062A (en) Carbon dioxide refrigeration system with compressors in two-stage arrangement
KR20020029597A (en) Multistage compression refrigerating machine for supplying refrigerant from intercooler to cool rotating machine and lubricating oil
US10101060B2 (en) Cooling system
US3246482A (en) Heat pumps
US4141708A (en) Dual flash and thermal economized refrigeration system
JP2000088431A (en) Brine cooler
US3108453A (en) Refrigerating apparatus including heat exchange stabilizer means
EP0924478A2 (en) Refrigeration system with integrated oil cooling heat exchanger
US4144717A (en) Dual flash economizer refrigeration system
JP2001272122A (en) Two-stage compression refrigerating unit
CA1205645A (en) Method of recirculating oil in refrigerating systems
CN109442778B (en) Air Conditioning System
JPS6230691Y2 (en)
JPH0317179Y2 (en)
CN212205122U (en) Oil-free compressor of ultralow-temperature water vapor capture pump system
JPS6022250B2 (en) vapor compression refrigeration equipment
CN211424747U (en) Oilless bearing liquid supply system and air conditioning unit
SU1079968A1 (en) Refrigerating machine
JPH0583666U (en) Refrigeration equipment
CN217763960U (en) Multi-handpiece parallel water chilling unit using shell-tube subcooler
JPH0763427A (en) Refrigerating plant