EP0180151A2 - Sous-refroidisseur condensant pour des systèmes frigorifiques - Google Patents

Sous-refroidisseur condensant pour des systèmes frigorifiques Download PDF

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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Withdrawn
Application number
EP85113527A
Other languages
German (de)
English (en)
Other versions
EP0180151A3 (fr
Inventor
Robert W. Adams
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0180151A2 publication Critical patent/EP0180151A2/fr
Publication of EP0180151A3 publication Critical patent/EP0180151A3/fr
Withdrawn legal-status Critical Current

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    • 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.

Landscapes

  • 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)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
  • Defrosting Systems (AREA)
  • Measuring Fluid Pressure (AREA)
EP85113527A 1984-10-29 1985-10-24 Sous-refroidisseur condensant pour des systèmes frigorifiques Withdrawn EP0180151A3 (fr)

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 (fr) 1986-05-07
EP0180151A3 EP0180151A3 (fr) 1986-06-11

Family

ID=24672084

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85113527A Withdrawn EP0180151A3 (fr) 1984-10-29 1985-10-24 Sous-refroidisseur condensant pour des systèmes frigorifiques

Country Status (4)

Country Link
EP (1) EP0180151A3 (fr)
JP (1) JPS61114057A (fr)
CN (1) CN85108065A (fr)
PT (1) PT81383B (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2193302A (en) * 1986-07-16 1988-02-03 Rejs Co Inc Refrigeration apparatus
EP0304281A2 (fr) * 1987-08-17 1989-02-22 Douglas C. Kann Inc. Dispositif frigorifique à économie d'énergie
WO1993020391A1 (fr) * 1992-04-02 1993-10-14 Ralph Chlebak Procede d'amelioration de l'efficacite d'un systeme de fefroidissement a circulation de liquide refrigerant
US9625191B2 (en) 2011-04-20 2017-04-18 Tokyo Electric Power Company, Incorporated Condensing apparatus
CN110849042A (zh) * 2019-11-29 2020-02-28 张家港市金腾化工机械制造有限公司 一种新型冷冻机组用u型冷凝器

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4727683B2 (ja) * 2008-03-21 2011-07-20 三菱重工コンプレッサ株式会社 ２段圧縮式冷凍システム
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)

* Cited by examiner, † Cited by third party
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 (fr) * 1982-05-03 1983-11-04 Carrier Corp Assemblage d'echangeur de chaleur pour un systeme de refrigeration

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU523481B2 (en) * 1977-08-29 1982-07-29 Carrier Corp. Thermal economized refrigeration system

Patent Citations (7)

* Cited by examiner, † Cited by third party
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 (fr) * 1982-05-03 1983-11-04 Carrier Corp Assemblage d'echangeur de chaleur pour un systeme de refrigeration

Cited By (9)

* Cited by examiner, † Cited by third party
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 (fr) * 1987-08-17 1989-02-22 Douglas C. Kann Inc. Dispositif frigorifique à économie d'énergie
EP0304281A3 (fr) * 1987-08-17 1989-05-17 Douglas C. Kann Inc. Dispositif frigorifique à économie d'énergie
AU612171B2 (en) * 1987-08-17 1991-07-04 Douglas C. Kann, Inc. Power saving refrigeration device
WO1993020391A1 (fr) * 1992-04-02 1993-10-14 Ralph Chlebak Procede d'amelioration de l'efficacite d'un systeme de fefroidissement a circulation de liquide refrigerant
US9625191B2 (en) 2011-04-20 2017-04-18 Tokyo Electric Power Company, Incorporated Condensing apparatus
CN110849042A (zh) * 2019-11-29 2020-02-28 张家港市金腾化工机械制造有限公司 一种新型冷冻机组用u型冷凝器

Also Published As

Publication number Publication date
JPS61114057A (ja) 1986-05-31
PT81383A (en) 1985-11-01
EP0180151A3 (fr) 1986-06-11
CN85108065A (zh) 1986-04-10
PT81383B (en) 1987-01-12

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