EP0504738A1 - Kühlsystem mit einem Nachkühlungsstromregelventil - Google Patents

Kühlsystem mit einem Nachkühlungsstromregelventil Download PDF

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Publication number
EP0504738A1
EP0504738A1 EP92104263A EP92104263A EP0504738A1 EP 0504738 A1 EP0504738 A1 EP 0504738A1 EP 92104263 A EP92104263 A EP 92104263A EP 92104263 A EP92104263 A EP 92104263A EP 0504738 A1 EP0504738 A1 EP 0504738A1
Authority
EP
European Patent Office
Prior art keywords
valve
refrigerant
chamber
condenser
compressor
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.)
Ceased
Application number
EP92104263A
Other languages
English (en)
French (fr)
Inventor
Jerome D. Powlas
William G. Nelson
Gary R. Peter
Sammie C. Beach, Jr.
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.)
White Consolidated Industries Inc
Original Assignee
White Consolidated Industries Inc
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
Priority claimed from US07/837,011 external-priority patent/US5201190A/en
Application filed by White Consolidated Industries Inc filed Critical White Consolidated Industries Inc
Publication of EP0504738A1 publication Critical patent/EP0504738A1/de
Ceased legal-status Critical Current

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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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/027—Condenser control arrangements
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part

Definitions

  • This invention relates to refrigeration systems, and more particularly to refrigeration systems used in household refrigerators and freezers.
  • Refrigeration systems for household refrigerators and freezers have heretofore been designed for low cost and high reliability, both of which require a simplicity of design, together with a minimum number of parts.
  • Typical refrigerators or freezers employ a vapor-compression system having a fractional horsepower, electric motor driven, hermetic compressor connected in a circuit with a condenser, an evaporator, an optional accumulator, and a refrigerant flow restriction between the condenser and the evaporator.
  • a relatively high duty cycle for the compressor run time while maintaining a sufficient reserve for high ambient temperature conditions.
  • a thermostat responsive to the temperature in the cooled cabinet is used to cycle the compressor as necessary to maintain the preselected temperature. Based on normal room temperatures and the absorption of heat into the cooled space through the insulation, the compressor duty cycle may run fifty percent to sixty percent, leaving a reserve but requiring continuous operation under very high ambient temperatures or frequent opening of the door for access to the interior of the cooled cabinet.
  • the flow restriction has been almost universally a capillary tube sized for optimal efficiency at a single set of conditions of ambient and internal cabinet temperature.
  • Capillary tubes used as the sole restriction offer the advantages of low cost, high reliability, and the added efficiency of being easily placed in heat exchange relationship with the return line from the evaporator to the compressor.
  • the capillary tube system which runs constantly at a single ambient temperature and constant load condition, is very efficient when the capillary tube is sized for these conditions.
  • the refrigerant at the condenser outlet where it enters the capillary tube is a saturated or slightly subcooled liquid.
  • This liquefied refrigerant flows through the capillary tube and undergoes a substantial pressure reduction until it enters the evaporator, where it is vaporized to absorb heat from the interior of the refrigerator or freezer.
  • the tube is usually soldered or otherwise placed in heat transfer relationship with the return line from the evaporator to the compressor. Because the common optimum conditions are such where the system operates at say a fifty percent duty cycle, the capillary tube is usually sized "loose" or with a reduced restriction which allows fast flooding of the evaporator during start-up and fast equalization of suction and discharge pressure during the OFF portion of the cycle.
  • the fast flooding of the evaporator allows the system to quickly reach a high running efficiency, thereby reducing the total compressor run time for the ON cycle.
  • this type of system tends to allow gas to enter the capillary tube and pass directly into the evaporator.
  • gas passes from the condenser to the evaporator it never goes through the phase change to a liquid and back to gas that is necessary to produce effective cooling in the evaporator. Not only does this load the compressor with an increased mass flow that does not refrigerate, but it also transports heat into the evaporator, to thereby reduce the efficiency of the system.
  • Valves of this type generally use a diaphragm or bellows operated by a refrigerant bulb that senses the temperature at some point in the system and opens or closes the valve located at the evaporator inlet to vary the amount of restriction at this point.
  • valves of this type are too large and much too expensive to be substituted for a capillary tube in small refrigeration systems.
  • the present invention provides an improved and more efficient refrigeration system for household refrigerators and freezers using a capillary tube restriction by adding a novel subcooling flow control valve between the condenser outlet and the entrance end of the capillary tube.
  • the capillary tube is sized as a significantly looser or less restrictive tube, and the pressure drop will be less than normal, with the rest of the drop taking place across the flow control valve.
  • the pressure drop across the capillary tube will remain proportional to the mass flow rate of the refrigerant, while the pressure drop across the flow control valve will be inversely proportional to the mass flow rate, since the valve opens more with increased mass flow which tends to be proportional to the amount of subcooling of the refrigerant at the outlet of the condenser. Since the flow control valve will close before the amount of subcooling at the condenser outlet drops below the minimum specified value, at no time during the cycle of operation of the system will gas enter the capillary tube.
  • a valve seat is mounted on the housing adjacent the outlet and is engageable by the valve element to seal and prevent any flow of refrigerant from the inlet to the outlet when the valve is fully closed.
  • the interior of the bellows defines a second chamber which is filled with a refrigerant in a saturated state, and the refrigerant may be either the same as that in the system or a fluid which has a greater saturation pressure than that of the refrigerant in the system.
  • the second chamber includes a tubular portion extending back into the inlet tube and exposed to the incoming refrigerant to ensure the most effective heat transfer between the system refrigerant and that in the second chamber, so that the second refrigerant and temperature will closely track that in the first chamber.
  • the minimum specified subcooling value or set point must be selected to be high enough in terms of the subcooling pressure in the surrounding refrigerant in the first chamber to ensure that the valve never opens unless there is a subcooled liquid in the first chamber and always closes before any gas can enter the capillary tube.
  • the set point cannot be too high or there will be difficulty in promoting the initial flow as the valve opens after the system has started.
  • a first chamber 36 is defined by the valve housing 26 and the two plates 32 and 34, and the operating valve mechanism is located in this chamber.
  • a boss 38 is formed on the side of inlet plate 32 within chamber 36, and serves as a seat for one end of an elongated bellows 40, whose other end is closed off by a base 43 of valve member 42, which in turn has a tip 46 adapted to engage the valve seat 35.
  • the bellows 40 is designed to allow free longitudinal expansion so that the valve member 42 can move axially within the chamber 36 in a direction toward and away from the valve seat 35 carried on outlet plate 34.
  • a support member or plate 156 extending transversely across the chamber a spaced distance from the partition member 151 to which it is rigidly secured at a peripheral flange 157.
  • the support member 156 includes a number of openings 158 to allow refrigerant to flow freely through the support member to a point adjacent the partition member 151.
  • an assembly comprising upper and lower diaphragm members 161 and 162 which form a sealed chamber 160.
  • the chamber 160 including the interior of tube 166 is sealed off from the system refrigerant and filled with a saturated charge of a refrigerant that may be the same as the system refrigerant or be one having a higher vapor pressure at the same temperature under saturated conditions.
  • the volume of the saturated refrigerant within the chamber 160 is carefully calibrated to insure the opening and closing of the valve by movement of the lower diaphragm member 162 and hence, the valve seal 167 toward and away from the valve seat 171.
  • the charge is sufficient that the valve is normally closed until the pressure and temperature within the chamber 153 and hence chamber 160 reaches a set point below the subcooling conditions to ensure that the chamber 153 is filled with a subcooled liquid from the condenser.
  • the refrigerant within the chamber 160 will be compressed to allow the lower diaphragm member 162 to move upwards to move the valve seal 169 away from seat 171.
  • the valve is opened and refrigerant can now pass into the capillary 128 and evaporator 129 to cool the cabinet 111.
  • the flow control valve 124 operates in modulating manner to insure that only a subcooled liquid is allowed to enter the capillary tube 128.

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)
EP92104263A 1991-03-19 1992-03-12 Kühlsystem mit einem Nachkühlungsstromregelventil Ceased EP0504738A1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US67139091A 1991-03-19 1991-03-19
US671390 1991-03-19
US837011 1992-02-24
US07/837,011 US5201190A (en) 1992-02-24 1992-02-24 Refrigerator with subcooling flow control valve

Publications (1)

Publication Number Publication Date
EP0504738A1 true EP0504738A1 (de) 1992-09-23

Family

ID=27100533

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92104263A Ceased EP0504738A1 (de) 1991-03-19 1992-03-12 Kühlsystem mit einem Nachkühlungsstromregelventil

Country Status (7)

Country Link
EP (1) EP0504738A1 (de)
JP (1) JPH0593557A (de)
KR (1) KR920018428A (de)
CN (1) CN1067113A (de)
AU (1) AU1283092A (de)
BR (1) BR9200919A (de)
TW (1) TW199202B (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0805318A2 (de) 1996-05-03 1997-11-05 Electrolux Espana, S.A. Kühlanlage
US9044757B2 (en) 2011-03-15 2015-06-02 Carclo Technical Plastics Limited Capillary fluid flow control

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE950887C (de) * 1954-03-20 1956-10-18 Daimler Benz Ag Thermostatanordnung
CH460412A (de) * 1967-01-02 1968-07-31 Gerdts Gustav F Kg Verdampfungsthermostat für Kondensatableiter
US4402455A (en) * 1981-08-28 1983-09-06 Leonard W. Suroff Automatic fluid control assembly
GB2121942A (en) * 1982-04-22 1984-01-04 Tokyo Shibaura Electric Co Compression-condensation refrigeration system
EP0272826A1 (de) * 1986-12-06 1988-06-29 Sanden Corporation Regelgerät für einen Kältekreislauf

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE950887C (de) * 1954-03-20 1956-10-18 Daimler Benz Ag Thermostatanordnung
CH460412A (de) * 1967-01-02 1968-07-31 Gerdts Gustav F Kg Verdampfungsthermostat für Kondensatableiter
US4402455A (en) * 1981-08-28 1983-09-06 Leonard W. Suroff Automatic fluid control assembly
GB2121942A (en) * 1982-04-22 1984-01-04 Tokyo Shibaura Electric Co Compression-condensation refrigeration system
EP0272826A1 (de) * 1986-12-06 1988-06-29 Sanden Corporation Regelgerät für einen Kältekreislauf

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0805318A2 (de) 1996-05-03 1997-11-05 Electrolux Espana, S.A. Kühlanlage
US5822999A (en) * 1996-05-03 1998-10-20 Electrolux Espana, S.A. Refrigeration system
US9044757B2 (en) 2011-03-15 2015-06-02 Carclo Technical Plastics Limited Capillary fluid flow control
US9352316B2 (en) 2011-03-15 2016-05-31 Carclo Technical Plastics Limited Capillary fluid flow control

Also Published As

Publication number Publication date
JPH0593557A (ja) 1993-04-16
CN1067113A (zh) 1992-12-16
BR9200919A (pt) 1992-11-17
KR920018428A (ko) 1992-10-22
AU1283092A (en) 1992-09-24
TW199202B (de) 1993-02-01

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