US3905202A - Refrigeration system - Google Patents
Refrigeration system Download PDFInfo
- Publication number
- US3905202A US3905202A US431757A US43175774A US3905202A US 3905202 A US3905202 A US 3905202A US 431757 A US431757 A US 431757A US 43175774 A US43175774 A US 43175774A US 3905202 A US3905202 A US 3905202A
- Authority
- US
- United States
- Prior art keywords
- pressure
- refrigerant
- evaporators
- line
- 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.)
- Expired - Lifetime
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Classifications
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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
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- 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
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
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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
- 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
- F25B2400/22—Refrigeration systems for supermarkets
-
- 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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
Definitions
- ABSTRACT A closed cycle refrigeration system comprising one or more compressors, a condenser exposed to ambient temperatures and of sufficient capacity to condense all of the gaseous refrigerant discharged from the compressors, a surge type receiver and one or more evaporators, is arranged so as to assure at least partial flooding of the condenser under normal ambient temperature conditions whereby the liquid refrigerant leaving the condenser is cooled to approximately ambient temperature prior to passage thereof to the evaporators.
- a sub-cooler using expanded refrigerant is not generally required and a substantial saving in the power requirements for operating the system is effected.
- the pressures to which the gaseous and liquid refrigerant are subjected throughout the system are maintained within optimum limits for more efficient and economical operation of the compressors and evaporators.
- an additional condenser is provided for use in reclaiming heat from the compressed refrigerant in which event the other condenser may function primarily to sub-cool the liquid refrigerant.
- Hot refrigerant gas from the compressor may also be used for defrosting the evaporators without adversely reducing the pressure at which liquid refrigerant is supplied to those evaporators operating on a refrigerating cycle.
- the temperature of the liquid refrigerant leaving the condenser heretofore has generally been in the neighborhood of 80F to 100F. It is then necessary for a portion of the liquid to be vaporized in the evaporator as flash gas in order to reduce its temperature to the operating temperature of the evaporator before any refrigeration effect can be attained by further evaporation thereof.
- an evaporative type sub-cooler is provided for reducing the temperature of the liquid refrigerant before it enters the evaporator but such sub-cooling equipment requires the expansion of refrigerant which must be made up by further operation of the compressor and the expenditure of considerable energy.
- the system includes a surge type receiver together with means for maintaining a controlled pressure in the receiver and in the liquid lines within limits which assure effective and efficient operation of the expansion valves and evaporators to which the refrigerant is supplied. At the same time such pressure is maintained below that at which gaseous refrigerant is supplied to the evaporators during defrosting operations. In this way liquid refrigerant discharged from the evaporators during defrost is readily returned to the liquid line without adverse reduction in the pressure of the refrigerant being supplied to those evaporators operating on a refrigerating cycle.
- the system normally is operated with substantial saving in its energy requirements and is adapted for use in large installations and when the reclaiming of heat for use in a building or enc osure is desired.
- FIG. I is a diagrammatic illustration of a simplified refrigeration system embodying the present invention.
- FIG. 2 is a diagrammatic illustration of a more complete refrigeration system embodying the present invention.
- the refrigeration system comprises a compressor 2, a condenser 4, a surge type receiver 6 and an evaporator 8.
- Refrigerant gas compressed in the compressor 2 is passed through a discharge line 10 to a condenser 4 exposed to ambient temperature as by being located on the roof of a market or other building in which refrigerated fixtures are used.
- the condenser 4 is of a size type and design rating such that it has a condensing capacity sufficient to assure condensation of all of the compressed refrigerant gas supplied thereto by the compressor 2 during normal temperature conditions to which it will be subjected.
- the condenser may be designed to have a higher rated condensing capacity for use in southern latitudes where the average ambient temperatures may be relatively higher than the design rating of the condenser used in systems employed in northern climates where the normal ambient temperature will be substantially lower.
- the liquid refrigerant leaving the condenser 4 flows through a drain line 12 to a liquid line 14 by which liquid refrigerant is supplied to one or more evaporators 8.
- the liquified refrigerant then passes through an expansion valve 16 for vaporization in the evaporator to refrigerate a fixture of any suitable or preferred type.
- the expanded and vaporized refrigerant gas leaving the evaporator 8 is returned to the compressor 2 through a return line 18.
- the liquid refrigerant receiver 6 communicates with the liquid line 14 by means of a connection 20 whereby a suitable amount of refrigerant may be stored and maintained in the system to assure continued operation thereof.
- a modulating pressure responsive valve 22 is located in the drain line 12 leading from the condenser 4 to liquid line 14 and is adjusted to respond to a predetermined pressure so as to maintain the head pressure of the compressor 2 at a desired operating level and sufficiently high to assure at least partial flooding of the condenser at all or at least most ambient temperatures to which the condenser will be subjected.
- the pressure to which liquid refrigerant in the receiver 6 and liquid line 14 is subjected is maintained relatively constant and sufficiently high to assure satisfactory and efficient operation of the expansion valve 16 associated with the evaporator 8.
- a pressure control line 26 extends from the discharge line 10 of the compressor 2 to the receiver 6 and is provided with a pressure responsive valve 28 adjusted to respond to a pressure below that which will actuate valve 22 in drain line 12 extending from the condenser to liquid line 14 but high enough to assure effective operation of the expansion valve 16 and evaporator 8.
- the system assures complete condensation of the gaseous refrigerant passing from the compressor 2 to the condenser 4 with at least partial flooding of the condenser at all, or at least most, ambient temperature conditions so that the liquid refrigerant passing from the condenser through drain line 12 to liquid line 14 will be reduced in temperature to approximately ambient temperature.
- the temperature of the ambient air passed over the condenser is 40F the liquid refrigerant passing to liquid line 14 will be about 40F.
- the pressure responsive valve 22 between drain line 12 and liquid line 14 may be adjusted to respond to a pressure of, say, 160 pounds per square inch.
- valve 22 will modulate to maintain a constant pressure in the condenser.
- the liquid refrigerant accumulated in the flooded portion of the condenser will be cooled during its retention therein to approximately ambient temperature (40F) and thereafter will pass through the valve 22 from drain line 12 to liquid line 14 at a relatively low temperature.
- the excess of liquid refrigerant over that immediately required for use in the evaporator or evaporators 8 will pass from the liquid line 14 through connection to the receiver 6 so as to be stored therein for use as required.
- the vapor therein when using R502 refrigerant, will reach saturation at a pressure of about 80 p.s.i. and the pressure of the liquid refrigerant being supplied to the evaporator 8 would only be 80 p.s.i. which is insufficient to assure effective and efficient operation of a typical expansion valve 16 associated therewith.
- the pressure of the liquid refrigerant in receiver 6 and liquid line 14 is maintained and controlled independently of the temperature of the receiver and the refrigerant therein.
- the pressure responsive valve 28 in pressure control line 26 extending from the compressor discharge line 10 to receiver 6 is adjusted to respond to a predetermined pressure, (say 150 p.s.i.) which is somewhat below that which will actuate valve 22 at the condenser outlet.
- a predetermined pressure say 150 p.s.i.
- the pressure applied to the liquid refrigerant in the receiver and liquid line 14 will be maintained constant and will not be significantly influenced by the temperature of the refrigerant entering and leaving the receiver. It can instead be maintained sufficiently high to insure efficient operation of the expansion valves and evaporators under all conditions of operation.
- the maintaining of proper and substantially constant pressure on the liquid refrigerant passing to the evaporator will be assured no matter where the receiver may be located and whether it is subjected to low ambient temperature or is positioned in a machine room with compressors and the like where its temperature may be relatively high.
- the condensing pressure and the compressor output pressure will be relatively low and the power expended in operating the system is materially reduced represent ing a substantial saving in the cost of operation.
- the ambient temperature is relatively high, say F, some power savings may be effected.
- the condensin g temperature will be about F and the condensing pressure and the compressor output pressure will be about 232 p.s.i. when using R502 refrigerant.
- the liquid refrigerant leaving the condenser will then be about 90F and be under a pressure above the p.s.i.
- valve 22 will then assume a fully open condition so that liquid refrigerant will pass directly from the condenser to the liquid line without restriction and little or no sub-cooling of the liquid refrigerant will take place. However, the liquid refrigerant in receiver 6 and liquid line 14 will then be under sufficient pressure to assure effective and efficient operation of the evaporator and its expansion valve throughout the refrigeration cycle. The pressure control line 26 and its valve 28 will then be unnecessary and will not function due to the adequate pressure developed in the receiver.
- FIG. 2 Under such conditions a more complete system may be employed as illustrated in FIG. 2.
- three compressors 40, 42 and 44 are connected in parallel with a common gas discharge header 46 from which compressed gaseous refrigerant is delivered through discharge line 48 to a condenser 50 positioned to be cooled by ambient air and of sufficient capacity to condense the entire refrigerant discharged from all three compressors.
- the condenser 50 delivers liquid refrigerant to a drain line 52 and liquid line 54 through pressure responsive valve 56.
- the liquid line 54 is connected to a surge type receiver 58 through connection 60 and is connected to the evaporators 62 and 64 through lines 66 and 68 respectively. Refrigerant from the evaporators is returned to the compressors through return lines 70 and 72 and a common return header 74.
- a heat reclaim coil 76 is connected to the discharge line 48 through a bi-pass line 78 and a thermostatically controlled solenoid valve 80.
- a condenser inlet pressure regulating valve 82 is connected in a line 84 extending from reclaim coil 76 to the condenser 50 through a check valve 86 and serves to maintain the desired head pressure in the compressor when the heat reclaim coil 76 is in use.
- a solenoid valve 88 and check valve 90 are located in the section 92 of the compressor discharge line 48 between the bi-pass line 78 and the condenser 50. The valve 88 closes when valve 80 is opened so as to assure flow of hot gas in series through heat reclaim coil 76 and condenser 50 when the heat reclaim coil is in use.
- valve 56 is adjusted to assure the desired condensing pressure in condenser 50 and assure at least partial flooding thereof under normal ambient temperature conditions.
- a pressure control line 98 having a pressure responsive valve 96 therein extends from discharge header 46 to receiver 58 and establishes the pressure at which the liquid refrigerant in receiver 58 and liquid line 54 will be maintained for delivery to the evaporators 62 and 64.
- the adjustment of valve 96 preferably is such that the pressure applied to the receiver and liquid line from gas discharge header 46 will be lower than the discharge pressure of the compressed refrigerant gas delivered to discharge line48 and condenser 50 so that there will be no danger of reverse flow of refrigerant from thereceiver to the condenser.
- any number of evaporators required for use in the system may be connected in this manner to the liquid line 54 and sufficient liquid refrigerant should be contained in the receiver 58 to assure delivery of liquid refrigerant to the liquid line 54 through connection 60 when the demands of the evaporator exceeds the supply of liquid refrigerant received from the condenser 50 at any period of operation.
- hot gas from the compressors may be delivered through the hot gas header 46 andbranch hot gas line 100 to whichever evaporators require defrosting.
- solenoid valve 102- in branch 103 of hot gas line 100 is opened to deliver hot refrigerant gas to'the line 70 whereas valve 105 in return line 73 is closed.
- the hot gas then flows through evaporator 62 in a direction reverse to that in which the expanding gas flows during the refrigerating operation whereby the temperature of the coils and fins of the evaporator is raised to defrost the same whereas the hot gas is cooled and at least partially condensed to a liquid.
- the resulting condensate then flows through bi-pass line 106 and check valve 107 about the expansion valve 94 and returns through line 66 to the liquid line 54.
- the liquid refrigerant resulting from the defrosting of the evaporator 62 is thus made available for use in refrigerating evaporator 64 and other evaporators employed in the system and to supplement the supply of liquid refrigerant being passed to such other evaporators.
- Such flow of the liquid refrigerant from defrosting evaporator 62 to liquid line 54 will take place by reason of the fact that the pressure applied to the liquid refrigerant in receiver 58 and liquid line 54 by pressure control line 98 and valve 96 is maintained below the pressure of the hot refrigerant gas supplied to the defrosting evaporators from branch hot gas line 100.
- a receiver pressure sensing line 110 is connected to the receiver 58 and extends to a diaphragm actuated regulating valve 112 located in the compressor discharge lines 48 at a point beyond the branch hot gas line 100.
- the regulating valve 112 is normally open but is operable to restrict flow of gas from the compressor through dis charge line 48 in the event the pressure in the discharge line should fall below the desired liquid'line pressure. In that event valve 1 12 will tend to close and modulate so as to increase the compressor head pressure and the pressure applied to the liquid refrigerant in the receiver and liquid lines through pressure control line 98 and pressure responsive valve 96. In this way an adequate and predetermined difference in pressure between the hot gas being used for defrosting purposes and the liquid refrigerant being supplied to the evaporators is assured under all conditions of operation of the system.
- the defrosting of one or a number of evaporators will further reduce the demand for liquid refrigerant whereas the hot gas required for the defrosting operation may be supplied by a single compressor with the result that the compressors 42 and 44 may both be cycled off while the single compressor 40 satisfies the refrigerant and defrosting requirements.
- the element 118 connected to compressor 42 is provided and designed to respond to a further reduction in the compressor inlet pressure to terminate operation of compressor 42. In this way still further reduction in the power required to operate the refrigerating system is effected.
- the system of FIG. 2 can be operated when employing only a single compressor during those periods when the condenser 50 is exposed to low ambient temperatures whereas only two compressors may be required during most normal operation and the third compressor will only be called into use during such times as the ambient temperature is abnormally high.
- the reduction in the power requirements of the system is thereby accomplished by utilizing the condenser 50 to effect a sub-cooling of the liquid refrigerant during all normal periods of operation and significant reduction in the energy requirements of the system is effected.
- a refrigerating system comprising a compressor having a discharge line and an intake line, a condenser connected to the discharge line of said compressor, a receiver for receiving condensed refrigerant from said condenser, a plurality of evaporators each provided with an expansion valve, a liquid line extending from said receiver to each of said expansion valves and evaporators, a return line extending from said evaporators to the intake line of the compressor, means for selectively defrosting said evaporators by the use of hot refrigerant gas from the discharge line of the compressor, a line extending from the discharge line of the compressor to said receiver and having a pressure reducing valve therein operable to maintain the pressure in said receiver and liquid line lower than the pressure in the I discharge line of the compressor, and means operable during defrost and responsive to a reduction in pressure in the receiver forincreasing the pressure in the discharge line of the compressor.
- a refrigerating system as defined in claim I wherein said means for maintaining liquid refrigerant in the receiver and liquid line under substantially constant pressure includes a line extending from said compressor discharge line to said receiver and has a valve therein responsive to a pressure below that which will actuate said pressure responsive valve in said liquid line.
- a refrigeration system as defined in claim 1 wherein means are provided for delivering gaseous refrigerant to each of said evaporators at a pressure exceeding the liquid line pressure for defrosting said evaporator.
- a refrigerating system as defined in claim 4 wherein there are a plurality of evaporators which may be defrosted by the delivery of gaseous refrigerant thereto, means for sensing the pressure of the refrigerant in the receiver, and valve means responsive to the operation of said sensing means operable to maintain the pressure at which refrigerant is discharged from the compressor above the pressure applied to liquid refrigerant in said liquid line.
- a refrigerating system as defined in claim 5 wherein said means for rendering at least one of said compressors inoperative is responsive to the pressure of refrigerant gas in a suction lineleading from said evaporators to said compressors.
- sensing means is operable to control the pressure at which gaseous refrigerant is discharged from said compressor and a pressure sensing line extends from said receiver to said sensing means to actuate the same.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Defrosting Systems (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US431757A US3905202A (en) | 1974-01-08 | 1974-01-08 | Refrigeration system |
CA217,248A CA1007062A (en) | 1974-01-08 | 1975-01-02 | Refrigeration system |
BR64/75A BR7500064A (pt) | 1974-01-08 | 1975-01-06 | Sistema de refrigeracao |
DE2500303A DE2500303C3 (de) | 1974-01-08 | 1975-01-07 | Kühlanlage |
GB648/75A GB1485583A (en) | 1974-01-08 | 1975-01-07 | Refrigeration system |
JP485175A JPS558747B2 (de) | 1974-01-08 | 1975-01-08 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US431757A US3905202A (en) | 1974-01-08 | 1974-01-08 | Refrigeration system |
Publications (1)
Publication Number | Publication Date |
---|---|
US3905202A true US3905202A (en) | 1975-09-16 |
Family
ID=23713292
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US431757A Expired - Lifetime US3905202A (en) | 1974-01-08 | 1974-01-08 | Refrigeration system |
Country Status (6)
Country | Link |
---|---|
US (1) | US3905202A (de) |
JP (1) | JPS558747B2 (de) |
BR (1) | BR7500064A (de) |
CA (1) | CA1007062A (de) |
DE (1) | DE2500303C3 (de) |
GB (1) | GB1485583A (de) |
Cited By (38)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4012921A (en) * | 1976-01-07 | 1977-03-22 | Emhart Industries, Inc. | Refrigeration and hot gas defrost system |
US4068494A (en) * | 1976-01-19 | 1978-01-17 | Kramer Daniel E | Power saving capacity control for air cooled condensers |
FR2414178A1 (fr) * | 1978-01-09 | 1979-08-03 | Emhart Ind | Systeme de refrigeration utilisant un agent refrigerant gazeux sature a des fins de degivrage |
US4167102A (en) * | 1975-12-24 | 1979-09-11 | Emhart Industries, Inc. | Refrigeration system utilizing saturated gaseous refrigerant for defrost purposes |
US4192149A (en) * | 1978-09-18 | 1980-03-11 | General Electric Company | Post condenser loop case heater controlled by ambient humidity |
US4193781A (en) * | 1978-04-28 | 1980-03-18 | Mcquay-Perfex Inc. | Head pressure control for heat reclaim refrigeration systems |
US4231229A (en) * | 1979-03-21 | 1980-11-04 | Emhart Industries, Inc. | Energy conservation system having improved means for controlling receiver pressure |
US4259848A (en) * | 1979-06-15 | 1981-04-07 | Voigt Carl A | Refrigeration system |
FR2482712A1 (fr) * | 1980-05-19 | 1981-11-20 | Emhart Ind | Systeme de refrigeration comportant un dispositif sensible a l'etat d'un fluide refrigerant |
US4356706A (en) * | 1980-08-05 | 1982-11-02 | Ronald Baumgarten | Thermally-integrated heat exchanger and refrigerator |
US4430866A (en) * | 1982-09-07 | 1984-02-14 | Emhart Industries, Inc. | Pressure control means for refrigeration systems of the energy conservation type |
US4507933A (en) * | 1980-05-05 | 1985-04-02 | Roman Chapa | System combining water heater and refrigeration unit |
US4535603A (en) * | 1984-07-02 | 1985-08-20 | Emhart Industries, Inc. | Highly energy efficient heat reclamation means for food display case refrigeration systems |
US4551989A (en) * | 1984-11-30 | 1985-11-12 | Gulf & Western Manufacturing Company | Oil equalization system for refrigeration compressors |
US4566288A (en) * | 1984-08-09 | 1986-01-28 | Neal Andrew W O | Energy saving head pressure control system |
US4621505A (en) * | 1985-08-01 | 1986-11-11 | Hussmann Corporation | Flow-through surge receiver |
US4735059A (en) * | 1987-03-02 | 1988-04-05 | Neal Andrew W O | Head pressure control system for refrigeration unit |
US4750337A (en) * | 1987-10-13 | 1988-06-14 | American Standard Inc. | Oil management in a parallel compressor arrangement |
EP0297221A2 (de) * | 1987-06-29 | 1989-01-04 | Behr GmbH & Co. | Vorrichtung zur Klimatisierung des Innenraums von Personenkraftwagen |
US4949551A (en) * | 1989-02-06 | 1990-08-21 | Charles Gregory | Hot gas defrost system for refrigeration systems |
US5092134A (en) * | 1989-08-18 | 1992-03-03 | Mitsubishi Denki Kabushiki Kaisha | Heating and cooling air conditioning system with improved defrosting |
US5289699A (en) * | 1991-09-19 | 1994-03-01 | Mayer Holdings S.A. | Thermal inter-cooler |
US5291749A (en) * | 1992-12-23 | 1994-03-08 | Schulak Edward R | Energy efficient domestic refrigeration system |
US5402651A (en) * | 1992-12-23 | 1995-04-04 | Schulak; Edward R. | Energy efficient domestic refrigeration system |
US5548968A (en) * | 1993-02-26 | 1996-08-27 | Daikin Industries, Ltd. | Refrigeraton apparatus |
US5666817A (en) * | 1996-12-10 | 1997-09-16 | Edward R. Schulak | Energy transfer system for refrigerator/freezer components |
US5743109A (en) * | 1993-12-15 | 1998-04-28 | Schulak; Edward R. | Energy efficient domestic refrigeration system |
US5775113A (en) * | 1992-12-23 | 1998-07-07 | Schulak; Edward R. | Energy efficient domestic refrigeration system |
US5791154A (en) * | 1992-12-23 | 1998-08-11 | Schulak; Edward R. | Energy transfer system for refrigeration components |
US5937662A (en) * | 1996-12-10 | 1999-08-17 | Edward R. Schulak | Energy transfer system for refrigerator/freezer components |
US5964101A (en) * | 1996-12-10 | 1999-10-12 | Edward R. Schulak | Energy transfer system for refrigerator/freezer components |
US6330804B1 (en) * | 1999-03-10 | 2001-12-18 | Hitachi, Ltd. | Refrigerating unit |
US20060225458A1 (en) * | 2005-04-12 | 2006-10-12 | Gaetan Lesage | Heat reclaim refrigeration system and method |
EP1734318A1 (de) * | 2005-06-13 | 2006-12-20 | Zanotti S.p.A. | Anlage und Verfahren für die Produktion von Kälte und für die Regelung der Lufttemperatur und Vorrichtung zum Wärmeaustausch für diese Anlage |
US20090145144A1 (en) * | 2007-12-07 | 2009-06-11 | Sanyo Electric Co., Ltd. | Controller and control method for refrigerating system |
US20130008182A1 (en) * | 2009-12-16 | 2013-01-10 | Brian Hrudka | Self-contained temperature controlled apparatus |
US10345011B2 (en) * | 2014-04-15 | 2019-07-09 | Gree Electric Appliances, Inc. Of Zhuhai | Refrigeration device |
US20210095908A1 (en) * | 2018-10-16 | 2021-04-01 | Tiax, Llc | Systems and methods for making ice |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5316941A (en) * | 1976-07-30 | 1978-02-16 | Hitachi Ltd | Freezer |
JPS5316943A (en) * | 1976-07-30 | 1978-02-16 | Hitachi Ltd | Freezer |
JPS61125569U (de) * | 1985-01-21 | 1986-08-07 | ||
CN110094904B (zh) * | 2019-03-18 | 2020-05-19 | 珠海格力电器股份有限公司 | 除霜系统、控制方法、装置及制冷设备 |
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US2874550A (en) * | 1955-05-19 | 1959-02-24 | Keeprite Products Ltd | Winter control valve arrangement in refrigerating system |
US2963877A (en) * | 1957-01-24 | 1960-12-13 | Kramer Trenton Co | Means for controlling high side pressure in refrigerating systems |
US3307369A (en) * | 1965-06-29 | 1967-03-07 | Westinghouse Electric Corp | Refrigeration system with compressor loading means |
US3324673A (en) * | 1965-07-19 | 1967-06-13 | Universal American Corp | Refrigeration system with check valve |
US3350896A (en) * | 1966-01-11 | 1967-11-07 | Westinghouse Electric Corp | Multiple evaporator refrigeration systems |
US3464226A (en) * | 1968-02-05 | 1969-09-02 | Kramer Trenton Co | Regenerative refrigeration system with means for controlling compressor discharge |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3427819A (en) * | 1966-12-22 | 1969-02-18 | Pet Inc | High side defrost and head pressure controls for refrigeration systems |
-
1974
- 1974-01-08 US US431757A patent/US3905202A/en not_active Expired - Lifetime
-
1975
- 1975-01-02 CA CA217,248A patent/CA1007062A/en not_active Expired
- 1975-01-06 BR BR64/75A patent/BR7500064A/pt unknown
- 1975-01-07 GB GB648/75A patent/GB1485583A/en not_active Expired
- 1975-01-07 DE DE2500303A patent/DE2500303C3/de not_active Expired
- 1975-01-08 JP JP485175A patent/JPS558747B2/ja not_active Expired
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2874550A (en) * | 1955-05-19 | 1959-02-24 | Keeprite Products Ltd | Winter control valve arrangement in refrigerating system |
US2963877A (en) * | 1957-01-24 | 1960-12-13 | Kramer Trenton Co | Means for controlling high side pressure in refrigerating systems |
US3307369A (en) * | 1965-06-29 | 1967-03-07 | Westinghouse Electric Corp | Refrigeration system with compressor loading means |
US3324673A (en) * | 1965-07-19 | 1967-06-13 | Universal American Corp | Refrigeration system with check valve |
US3350896A (en) * | 1966-01-11 | 1967-11-07 | Westinghouse Electric Corp | Multiple evaporator refrigeration systems |
US3464226A (en) * | 1968-02-05 | 1969-09-02 | Kramer Trenton Co | Regenerative refrigeration system with means for controlling compressor discharge |
Cited By (46)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4167102A (en) * | 1975-12-24 | 1979-09-11 | Emhart Industries, Inc. | Refrigeration system utilizing saturated gaseous refrigerant for defrost purposes |
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EP1734318A1 (de) * | 2005-06-13 | 2006-12-20 | Zanotti S.p.A. | Anlage und Verfahren für die Produktion von Kälte und für die Regelung der Lufttemperatur und Vorrichtung zum Wärmeaustausch für diese Anlage |
US20090145144A1 (en) * | 2007-12-07 | 2009-06-11 | Sanyo Electric Co., Ltd. | Controller and control method for refrigerating system |
US8397526B2 (en) * | 2007-12-07 | 2013-03-19 | Sanyo Electric Co., Ltd. | Controller and control method for refrigerating system |
US20130008182A1 (en) * | 2009-12-16 | 2013-01-10 | Brian Hrudka | Self-contained temperature controlled apparatus |
US10345011B2 (en) * | 2014-04-15 | 2019-07-09 | Gree Electric Appliances, Inc. Of Zhuhai | Refrigeration device |
US20210095908A1 (en) * | 2018-10-16 | 2021-04-01 | Tiax, Llc | Systems and methods for making ice |
Also Published As
Publication number | Publication date |
---|---|
GB1485583A (en) | 1977-09-14 |
BR7500064A (pt) | 1975-11-04 |
DE2500303B2 (de) | 1980-04-30 |
CA1007062A (en) | 1977-03-22 |
JPS558747B2 (de) | 1980-03-05 |
JPS50113854A (de) | 1975-09-06 |
DE2500303C3 (de) | 1980-12-18 |
DE2500303A1 (de) | 1975-07-10 |
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Legal Events
Date | Code | Title | Description |
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AS | Assignment |
Owner name: JEPSON REFRIGERATION CORPORATION, 340 BUTTERFIELD Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:EMHARDT INDUSTRIES, INC.;REEL/FRAME:004472/0442 Effective date: 19850627 |
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Owner name: FIRST NATIONAL BANK OF BOSTON THE Free format text: SECURITY INTEREST;ASSIGNOR:HILL REFRIGERATION CORPORATION, A CORP. OF DE.;REEL/FRAME:004599/0811 Effective date: 19850627 Owner name: FIRST NATIONAL BANK OF BOSTON THE,STATELESS Free format text: SECURITY INTEREST;ASSIGNOR:HILL REFRIGERATION CORPORATION, A CORP. OF DE.;REEL/FRAME:004599/0811 Effective date: 19850627 |
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Owner name: HILL REFRIGERATION CORPORATION, A CORP. OF CA. Free format text: MERGER;ASSIGNOR:JEPSON REFRIGERATION CORPORATION (MERGED INTO);REEL/FRAME:004834/0614 Effective date: 19850627 Owner name: HILL REFRIGERATION CORPORATION, A CORP. OF CA., CA Free format text: MERGER;ASSIGNOR:JEPSON REFRIGERATION CORPORATION (MERGED INTO);REEL/FRAME:004834/0614 Effective date: 19850627 |
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Owner name: MANUFACTURING HANOVER TRUST COMPANY Free format text: SECURITY INTEREST;ASSIGNOR:FALCON MANUFACTURING, INC., A CORP. OF DE;REEL/FRAME:005580/0638 Effective date: 19910109 |