EP0180151A2 - Condensing sub-cooler for refrigeration systems - Google Patents
Condensing sub-cooler for refrigeration systems Download PDFInfo
- Publication number
- EP0180151A2 EP0180151A2 EP85113527A EP85113527A EP0180151A2 EP 0180151 A2 EP0180151 A2 EP 0180151A2 EP 85113527 A EP85113527 A EP 85113527A EP 85113527 A EP85113527 A EP 85113527A EP 0180151 A2 EP0180151 A2 EP 0180151A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- cooler
- sub
- refrigeration system
- liquid
- liquid refrigerant
- 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.)
- Withdrawn
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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
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
-
- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
Definitions
- the present invention relates to closed circuit refrigeration systems having a metering device such as an expansion valve, a condenser, a compressor, and an evaporator. More particularly, the invention relates to a sub-cooler for a refrigeration system which cools the liquid and condenses vapor in the liquid line prior to the liquids passing through the metering device.
- a metering device such as an expansion valve, a condenser, a compressor, and an evaporator. More particularly, the invention relates to a sub-cooler for a refrigeration system which cools the liquid and condenses vapor in the liquid line prior to the liquids passing through the metering device.
- Refrigeration systems consume a significant portion of all electrical energy generated in the United States. Because the systems have to operate at different ambient temperatures, they seldom operate at the most efficient level. Accordingly, a substantial amount of energy is wasted.
- any vapor in the line significantly decreases the efficiency of the system by decreasing the amount of liquid which can pass through the metering device to the evaporator.
- the present invention provides a fixed, mechanical condensing sub-cooler for condensing vaporized refrigerant and for sub-cooling the liquid prior to its entering a metering device such as an expansion valve in a closed- circuit refrigeration system.
- the sub-cooler comprises a shell forming a chamber having an inlet and an outlet and is placed in the liquid refrigeration line immediately preceding the metering device in the direction of flow.
- the inlet includes means for reducing the pressure of the liquid refrigerant so as to effectuate cooling which causes any vapor present in the system to condense.
- the pressure reducing means comprises a length of tubing attached to the inlet to the shell, said tubing including a plurality of orifices through which refrigerant is discharged into the chamber in the shell.
- a liquid level is maintained within the sub-cooler and the outlet is connected below the level of the liquid such that vapor is not passed through the outlet to the metering device.
- a reduced refrigerant charge can be used which permits the system to be operated below the standard design temperature and pressure such that a given quantity of refrigerant will have a greater cooling effect as it passes through the evaporator. Accordingly, systems utilizing the present invention can provide the same amount of cooling with less power consumption than conventional systems.
- the present invention is directed to a fixed, mechanical condenser sub-cooler for closed circuit refrigeration systems.
- the sub-cooler is placed in the liquid refrigerant line immediately prior to the metering device, which can be a conventional expansion valve or capillary tube system.
- the sub-cooler cools the liquid refrigerant prior to its entering the metering device so as to increase the efficiency of the system, and condenses vapor formed in the liquid line through absorption of ambient heat along the length of the liquid line caused by a reduction in the pressure head between the condenser and metering device.
- FIG. 3 schematically illustrates a conventional refrigeration system, generally designated at 10, into which a sub-cooler 12 of the present invention has been incorporated.
- Refrigeration system 10 includes a metering device 14 which can be an expansion valve, capillary tube, or any other type of conventional metering device used in refrigeration circuits.
- a low pressure liquid line 16 extends from metering device 14 to evaporator 18 where the refrigerant is allowed to vaporize and absorb heat. From the evaporator, the vaporized refrigerant passes through line 20 to compressor unit 22.
- Compressor unit 22 comprises a compressor 24 which is powered by a motor 26. Either centrifugal or positive displacement compressor units can be utilized in circuits incorporating the present invention.
- condenser 30 From the compressor unit, high pressure vaporized refrigerant is passed through line 28 to a condenser 30 in which the refrigerant is condensed. While condenser 30 is illustrated as an air cooled condenser, it will be appreciated that the system can also utilize water cooled units or any other type of conventional condenser.
- the liquefied refrigerant passes through line 32 to a receiver 34.
- a receiver 34 As will be more fully discussed hereinafter, when utilizing the present invention it is possible to eliminate receiver 34 from the refrigeration system.
- the liquefied refrigerant passes through line 36 to sub-cooler 12. Any vapor which is formed as the refrigerant passes through lines 32 and 36 is condensed in sub-cooler 12 before the refrigerant passes to metering device 14.
- Sub-cooler 12 includes a shell 40 having an inlet connected to line 36 coming from the receiver or condenser and an outlet connected to the line 38 leading to the metering device.
- shell 40 is formed from a cylindrical tube 42 having end caps 44 and 46.
- Shell 40 defines a chamber which is partially filled with liquid refrigerant such that there is a liquid level 56 and a vapor space 55.
- a portion of line 36 extends into shell 40 and is bent into a U-shaped configuration to form a spray bar 48 which is positioned in vapor space 55.
- the end of spray bar 48 includes a cap or plug 50.
- a plurality of orifices 52 are formed along a portion of the length of spray bar 48 to act as nozzles. As the liquid refrigerant 54 sprays out of orifices 52 its pressure is reduced which creates a cooling effect. This cooling causes vapor in the line to condense.
- sub-cooler 12 The liquid refrigerant 56 in the bottom of sub-cooler 12 is withdrawn through outlet 58 into line 38 where it passes to the metering device. If sub-cooler 12 is properly sized, receiver 34 (see Figure 3) can be eliminated from the refrigeration circuit and the chamber formed by shell 40 of sub-cooler 12 can serve as the receiver.
- a plate 60 is positioned within shell 48 between spray bar 48 and the liquid 56.
- Plate 60 includes a plurality of orifices 62 through which the liquid refrigerant can pass. Plate 60 serves to avoid splashing of the liquid 56 which might be caused by the spray 54.
- plate 60 is not essential to the operation of sub-cooler 12 and can be eliminated if desired.
- the number and size of the orifices 52 in spray bar 48 are adjusted such that a pressure drop of from about 3 to about 6 pounds per square inch is created across sub-cooler 12.
- the preferred pressure drop is about 5 pounds per square inch when using a refrigerant such as 12, 22, 500, 502, or F-11. This pressure drop has been found to be sufficient to condense any vapor formed in the liquid line. Because vapor is condensed and only liquid refrigerant is withdrawn from sub-cooler 12 it is possible to reduce the refrigerant charge and thus the operating pressure and temperature of the refrigeration system. This allows a given volume of refrigerant to have a greater cooling effect as it passes through the evaporator downstream from the metering device. Accordingly, the refrigeration system is more efficient and less power is required to provide the same cooling effect.
- Figure 4 illustrates the embodiment of Figures 1 and 2 as it would operate if installed in a vertical position.
- the inlet line 36 is arranged to enter the top of shell 40 and the outlet 58 is positioned in the bottom of shell 40.
- the level of the liquid 56 is generally adjusted such that it is below the orifices 52. Should the liquid level rise so as to cover the bottom most of orifices 52, the sub-cooler will still operate but its cooling capacity will be reduced.
- Sub-cooler 112 includes a shell 140 which is formed from a piece of cylindrical tubing 142 with end caps 144 and 146.
- Line 36 passes through upper end cap 144 and is connected to a spray bar 148 by a T-connection.
- Spray bar 148 includes a plurality of orifices 152 through which liquid refrigerant 154 is sprayed.
- Liquid refrigerant 156 is maintained at a level in the bottom of shell 140 and is removed through line 38.
- the present invention provides a novel fixed, mechanical condenser which can be added into substantially any refrigeration system to reduce its normal power requirements.
- the sub-cooler provides for the condensation of any vapor which may form in the line leading from the condenser to the metering device such that a reduced refrigerant charge can be used.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Defrosting Systems (AREA)
- Measuring Fluid Pressure (AREA)
- Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
Abstract
Description
- The present invention relates to closed circuit refrigeration systems having a metering device such as an expansion valve, a condenser, a compressor, and an evaporator. More particularly, the invention relates to a sub-cooler for a refrigeration system which cools the liquid and condenses vapor in the liquid line prior to the liquids passing through the metering device.
- Refrigeration systems consume a significant portion of all electrical energy generated in the United States. Because the systems have to operate at different ambient temperatures, they seldom operate at the most efficient level. Accordingly, a substantial amount of energy is wasted.
- One problem which causes a portion of this inefficiency is the formation of vapor in the liquid refrigerant line between the condenser and the metering device. In many systems, there is a long piece of tubing between the condenser and the metering device. As the liquid refrigerant passes through this tubing it can absorb heat if the ambient temperature is high, causing vapor to form.
- Additionally, pressure reductions in the line as a result of friction or decreases in the head pressure as the refrigerant moves further from the compressor and condenser can contribute to the formation of vapor. Because the metering devices generally are sized for passing only liquid, any vapor in the line significantly decreases the efficiency of the system by decreasing the amount of liquid which can pass through the metering device to the evaporator.
- Various approaches procedures have been developed and utilized to overcome the problem of vapor formation. One approach involves increasing the pressure in the liquid refrigerant line to a point that no vapor will form under most or all operating conditions which the system is likely to encounter. However, this requires a larger compressor than would otherwise be necessary, resulting in a greater use of power to run the compressor.
- Another approach is disclosed in U.S. Patent No. 4,259,848 to Voigt. In this system, vapor formed by exposure of the liquid refrigerant conduit to ambient conditions is withdrawn from a receiver by a dual suction compressor, and the refrigerant approaching the expansion valve is adiabatically cooled in a heat exchanger to liquefy any additional vapor formed by the withdrawal of vaporized refrigerant from the high pressure portion of the circuit. While this system works under some circumstances, it still has several drawbacks. For example, it cannot be used effectively on refrigeration systems utilizing a hot gas defrost. Additionally, a complicated valving mechanism between the receiver and the compressor is required to control the flow of vaporized refrigerant from the high pressure line back to the compressor. Also, the metering device in such a system must be an expansion valve.
- Accordingly, it would be a significant advancement in the art to provide a fixed, mechanical condensing sub-cooler which could be used in closed circuit refrigeration systems to cool the liquid refrigerant and to condense vapor formed in the high pressure liquid line before it passes through the metering device. It would be particularly advantageous to provide such a system which is simple in construction and operation, and which is effective. Such a system is disclosed and claimed herein.
- The present invention provides a fixed, mechanical condensing sub-cooler for condensing vaporized refrigerant and for sub-cooling the liquid prior to its entering a metering device such as an expansion valve in a closed- circuit refrigeration system. The sub-cooler comprises a shell forming a chamber having an inlet and an outlet and is placed in the liquid refrigeration line immediately preceding the metering device in the direction of flow. The inlet includes means for reducing the pressure of the liquid refrigerant so as to effectuate cooling which causes any vapor present in the system to condense. In a preferred embodiment, the pressure reducing means comprises a length of tubing attached to the inlet to the shell, said tubing including a plurality of orifices through which refrigerant is discharged into the chamber in the shell. A liquid level is maintained within the sub-cooler and the outlet is connected below the level of the liquid such that vapor is not passed through the outlet to the metering device.
- Inasmuch as the present invention condenses any vapor which is formed in the liquid refrigerant line immediately prior to the liquids entering the metering device, a reduced refrigerant charge can be used which permits the system to be operated below the standard design temperature and pressure such that a given quantity of refrigerant will have a greater cooling effect as it passes through the evaporator. Accordingly, systems utilizing the present invention can provide the same amount of cooling with less power consumption than conventional systems.
-
- Figure 1 is a cross-sectional view of a preferred embodiment of the sub-cooler of the present invention mounted in a horizontal position.
- Figure 2 is a cross-sectional view of the embodiment illustrated in Figure 1 taken along the line 2-2.
- Figure 3 is a schematic view of a refrigeration circuit including the present invention.
- Figure 4 is a cross-sectional view of the embodiment illustrated in Figure 1 mounted in a vertical position.
- Figure 5 is a cross-sectional view of a second preferred embodiment of the present invention.
- The present invention is directed to a fixed, mechanical condenser sub-cooler for closed circuit refrigeration systems. The sub-cooler is placed in the liquid refrigerant line immediately prior to the metering device, which can be a conventional expansion valve or capillary tube system. The sub-cooler cools the liquid refrigerant prior to its entering the metering device so as to increase the efficiency of the system, and condenses vapor formed in the liquid line through absorption of ambient heat along the length of the liquid line caused by a reduction in the pressure head between the condenser and metering device.
- Reference is first made to Figure 3 which schematically illustrates a conventional refrigeration system, generally designated at 10, into which a
sub-cooler 12 of the present invention has been incorporated. -
Refrigeration system 10 includes ametering device 14 which can be an expansion valve, capillary tube, or any other type of conventional metering device used in refrigeration circuits. A low pressureliquid line 16 extends frommetering device 14 toevaporator 18 where the refrigerant is allowed to vaporize and absorb heat. From the evaporator, the vaporized refrigerant passes throughline 20 tocompressor unit 22.Compressor unit 22 comprises acompressor 24 which is powered by amotor 26. Either centrifugal or positive displacement compressor units can be utilized in circuits incorporating the present invention. - From the compressor unit, high pressure vaporized refrigerant is passed through
line 28 to acondenser 30 in which the refrigerant is condensed. Whilecondenser 30 is illustrated as an air cooled condenser, it will be appreciated that the system can also utilize water cooled units or any other type of conventional condenser. - From the condenser, the liquefied refrigerant passes through
line 32 to areceiver 34. As will be more fully discussed hereinafter, when utilizing the present invention it is possible to eliminatereceiver 34 from the refrigeration system. - From
receiver 34, the liquefied refrigerant passes throughline 36 to sub-cooler 12. Any vapor which is formed as the refrigerant passes throughlines sub-cooler 12 before the refrigerant passes tometering device 14. - Reference is next made to Figure 1, in which a preferred embodiment of
sub-cooler 12 is illustrated in a cross-sectional view.Sub-cooler 12 includes ashell 40 having an inlet connected toline 36 coming from the receiver or condenser and an outlet connected to theline 38 leading to the metering device. In the illustrated embodiment,shell 40 is formed from acylindrical tube 42 havingend caps liquid level 56 and avapor space 55. - In the illustrated embodiment, a portion of
line 36 extends intoshell 40 and is bent into a U-shaped configuration to form aspray bar 48 which is positioned invapor space 55. The end ofspray bar 48 includes a cap orplug 50. A plurality oforifices 52 are formed along a portion of the length ofspray bar 48 to act as nozzles. As theliquid refrigerant 54 sprays out oforifices 52 its pressure is reduced which creates a cooling effect. This cooling causes vapor in the line to condense. - The
liquid refrigerant 56 in the bottom ofsub-cooler 12 is withdrawn throughoutlet 58 intoline 38 where it passes to the metering device. Ifsub-cooler 12 is properly sized, receiver 34 (see Figure 3) can be eliminated from the refrigeration circuit and the chamber formed byshell 40 ofsub-cooler 12 can serve as the receiver. - In the illustrated embodiment, a
plate 60 is positioned withinshell 48 betweenspray bar 48 and theliquid 56.Plate 60 includes a plurality oforifices 62 through which the liquid refrigerant can pass.Plate 60 serves to avoid splashing of theliquid 56 which might be caused by thespray 54. However,plate 60 is not essential to the operation ofsub-cooler 12 and can be eliminated if desired. - The number and size of the
orifices 52 inspray bar 48 are adjusted such that a pressure drop of from about 3 to about 6 pounds per square inch is created acrosssub-cooler 12. The preferred pressure drop is about 5 pounds per square inch when using a refrigerant such as 12, 22, 500, 502, or F-11. This pressure drop has been found to be sufficient to condense any vapor formed in the liquid line. Because vapor is condensed and only liquid refrigerant is withdrawn from sub-cooler 12 it is possible to reduce the refrigerant charge and thus the operating pressure and temperature of the refrigeration system. This allows a given volume of refrigerant to have a greater cooling effect as it passes through the evaporator downstream from the metering device. Accordingly, the refrigeration system is more efficient and less power is required to provide the same cooling effect. - Reference is next made to Figure 4 which illustrates the embodiment of Figures 1 and 2 as it would operate if installed in a vertical position. The
inlet line 36 is arranged to enter the top ofshell 40 and theoutlet 58 is positioned in the bottom ofshell 40. The level of the liquid 56 is generally adjusted such that it is below theorifices 52. Should the liquid level rise so as to cover the bottom most oforifices 52, the sub-cooler will still operate but its cooling capacity will be reduced. - Referring now to Figure 5, a second preferred embodiment of the present invention is illustrated in cross section.
Sub-cooler 112 includes ashell 140 which is formed from a piece ofcylindrical tubing 142 withend caps Line 36 passes throughupper end cap 144 and is connected to aspray bar 148 by a T-connection.Spray bar 148 includes a plurality of orifices 152 through whichliquid refrigerant 154 is sprayed. -
Liquid refrigerant 156 is maintained at a level in the bottom ofshell 140 and is removed throughline 38. - As can be seen from the foregoing, the present invention provides a novel fixed, mechanical condenser which can be added into substantially any refrigeration system to reduce its normal power requirements. The sub-cooler provides for the condensation of any vapor which may form in the line leading from the condenser to the metering device such that a reduced refrigerant charge can be used.
- While the invention has been described with respect to the presently preferred embodiments, it will be appreciated that other modifications or changes could be made without departing from its scope or essential characteristics. For example, in the embodiment illustrated in Figure 5 a plurality of spray bars could be used or the spray bar could be configurated as a disk with a plurality of orifices. Changes could also be made to the shape of the shell of the sub-cooler. Additionally, the system can be operated with or without a plate between the spray bar and the surface of the liquid refrigerant. Accordingly, all changes or modifications which come within the meaning and range of equivalency of the claims are to be embraced within their scope.
Claims (14)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US66591684A | 1984-10-29 | 1984-10-29 | |
US665916 | 1984-10-29 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0180151A2 true EP0180151A2 (en) | 1986-05-07 |
EP0180151A3 EP0180151A3 (en) | 1986-06-11 |
Family
ID=24672084
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP85113527A Withdrawn EP0180151A3 (en) | 1984-10-29 | 1985-10-24 | Condensing sub-cooler for refrigeration systems |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0180151A3 (en) |
JP (1) | JPS61114057A (en) |
CN (1) | CN85108065A (en) |
PT (1) | PT81383B (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2193302A (en) * | 1986-07-16 | 1988-02-03 | Rejs Co Inc | Refrigeration apparatus |
EP0304281A2 (en) * | 1987-08-17 | 1989-02-22 | Douglas C. Kann Inc. | Power saving refrigeration device |
WO1993020391A1 (en) * | 1992-04-02 | 1993-10-14 | Ralph Chlebak | Enhancing efficiency of refrigerant-circulating cooling system |
US9625191B2 (en) | 2011-04-20 | 2017-04-18 | Tokyo Electric Power Company, Incorporated | Condensing apparatus |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4727683B2 (en) * | 2008-03-21 | 2011-07-20 | 三菱重工コンプレッサ株式会社 | Two-stage compression refrigeration system |
DK178682B1 (en) * | 2015-04-15 | 2016-11-07 | Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland | A large turbocharged self-igniting two-stroke internal combustion engine and a sealing ring therefore |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2183346A (en) * | 1937-04-01 | 1939-12-12 | Westinghouse Electric & Mfg Co | Refrigeration apparatus and method |
US2489680A (en) * | 1946-05-15 | 1949-11-29 | Philco Corp | Refrigerant circulating system |
US2518587A (en) * | 1947-04-11 | 1950-08-15 | Philco Corp | Refrigerant flow control |
US3553974A (en) * | 1968-11-29 | 1971-01-12 | Carrier Corp | Refrigeration system |
US4142381A (en) * | 1977-08-29 | 1979-03-06 | Carrier Corporation | Flash type subcooler |
US4207749A (en) * | 1977-08-29 | 1980-06-17 | Carrier Corporation | Thermal economized refrigeration system |
FR2526137A1 (en) * | 1982-05-03 | 1983-11-04 | Carrier Corp | HEAT EXCHANGER ASSEMBLY FOR A REFRIGERATION SYSTEM |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6053264B2 (en) * | 1977-08-29 | 1985-11-25 | キャリア コ−ポレ−ション | Heat saving refrigeration system |
-
1985
- 1985-10-24 EP EP85113527A patent/EP0180151A3/en not_active Withdrawn
- 1985-10-28 CN CN198585108065A patent/CN85108065A/en active Pending
- 1985-10-28 PT PT8138385A patent/PT81383B/en unknown
- 1985-10-29 JP JP24258985A patent/JPS61114057A/en active Pending
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2183346A (en) * | 1937-04-01 | 1939-12-12 | Westinghouse Electric & Mfg Co | Refrigeration apparatus and method |
US2489680A (en) * | 1946-05-15 | 1949-11-29 | Philco Corp | Refrigerant circulating system |
US2518587A (en) * | 1947-04-11 | 1950-08-15 | Philco Corp | Refrigerant flow control |
US3553974A (en) * | 1968-11-29 | 1971-01-12 | Carrier Corp | Refrigeration system |
US4142381A (en) * | 1977-08-29 | 1979-03-06 | Carrier Corporation | Flash type subcooler |
US4207749A (en) * | 1977-08-29 | 1980-06-17 | Carrier Corporation | Thermal economized refrigeration system |
FR2526137A1 (en) * | 1982-05-03 | 1983-11-04 | Carrier Corp | HEAT EXCHANGER ASSEMBLY FOR A REFRIGERATION SYSTEM |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2193302A (en) * | 1986-07-16 | 1988-02-03 | Rejs Co Inc | Refrigeration apparatus |
AU588703B2 (en) * | 1986-07-16 | 1989-09-21 | Rejs Co., Inc. | Refrigeration apparatus |
GB2193302B (en) * | 1986-07-16 | 1991-02-20 | Rejs Co Inc | Refrigeration apparatus |
EP0304281A2 (en) * | 1987-08-17 | 1989-02-22 | Douglas C. Kann Inc. | Power saving refrigeration device |
EP0304281A3 (en) * | 1987-08-17 | 1989-05-17 | Douglas C. Kann Inc. | Power saving refrigeration device |
AU612171B2 (en) * | 1987-08-17 | 1991-07-04 | Douglas C. Kann, Inc. | Power saving refrigeration device |
WO1993020391A1 (en) * | 1992-04-02 | 1993-10-14 | Ralph Chlebak | Enhancing efficiency of refrigerant-circulating cooling system |
US9625191B2 (en) | 2011-04-20 | 2017-04-18 | Tokyo Electric Power Company, Incorporated | Condensing apparatus |
Also Published As
Publication number | Publication date |
---|---|
CN85108065A (en) | 1986-04-10 |
JPS61114057A (en) | 1986-05-31 |
EP0180151A3 (en) | 1986-06-11 |
PT81383B (en) | 1987-01-12 |
PT81383A (en) | 1985-11-01 |
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