US20110259041A1 - High efficiency condenser - Google Patents
High efficiency condenser Download PDFInfo
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- US20110259041A1 US20110259041A1 US12/764,149 US76414910A US2011259041A1 US 20110259041 A1 US20110259041 A1 US 20110259041A1 US 76414910 A US76414910 A US 76414910A US 2011259041 A1 US2011259041 A1 US 2011259041A1
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- Prior art keywords
- condenser
- refrigerator
- phase change
- heat exchanger
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D23/00—General constructional features
- F25D23/003—General constructional features for cooling refrigerating machinery
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
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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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/042—Details of condensers of pcm condensers
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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
- F25B2600/00—Control issues
- F25B2600/11—Fan speed control
- F25B2600/111—Fan speed control of condenser fans
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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
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D2020/0004—Particular heat storage apparatus
- F28D2020/0013—Particular heat storage apparatus the heat storage material being enclosed in elements attached to or integral with heat exchange conduits
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/14—Thermal energy storage
Definitions
- the present invention relates to a refrigeration system with an improved condenser configuration.
- the refrigeration system of the present invention incorporates a high efficiency condenser in which, in one embodiment, a phase change material is incorporated within the condenser to assist in cooling the condenser during operation and particularly during pull-down operation to improve the cooling capacity of a compressor.
- a coaxial tube carrying the refrigerant through the condenser includes an inner conduit for the refrigerant and a coaxially arranged outer jacket with phase change material for extracting heat from the compressed refrigerant.
- a secondary extended condenser is provided in addition to the condenser having phase change material.
- a condenser in yet another embodiment, includes an extended surface and a secondary condenser, both of which include fans which can be operated in the high speed (turbo) mode during pull-down of a refrigeration system for providing sufficient cooling capacity during a pull-down mode of operation.
- the improved efficiency condenser system of the present system is particularly suited for use with a linear compressor, although it can be employed with conventional rotary compressors as well.
- FIG. 1 is a perspective view of a side-by-side refrigerator freezer incorporating the improved condenser of the present invention
- FIG. 2 is a schematic view of the components of the system of the present invention including a preferred embodiment of a compressor and condenser system;
- FIG. 3 is an enlarged schematic view of a linear compressor employed in the preferred embodiment of the invention.
- FIG. 4 is an enlarged fragmentary front elevational view of a coaxial condenser employing a phase change material
- FIG. 5 is an enlarged fragmentary cross-sectional view, taken along section lines V-V of FIG. 4 ;
- FIG. 6 is a fragmentary, front elevational view of an alternative condenser structure in which a phase change material is coaxially associated with the refrigerant line in the condenser;
- FIG. 7 is a schematic view of the components of an alternative embodiment of a condenser system of the present invention.
- FIG. 8 is another alternative embodiment of a condenser system embodying the present invention.
- FIG. 9 is another alternative embodiment of a condenser of the present invention.
- FIGS. 10A-10B are a table illustrating the operational modes of the preferred embodiments of the invention.
- FIG. 11 is a graph comparing typical cycles of operation of systems with and without the condenser system of the present invention.
- FIG. 1 there is shown a refrigerator freezer 10 embodying the present invention, which includes a side-by-side refrigerated cabinet 12 and a freezer cabinet 14 .
- Each of the cabinets 12 and 14 include side walls 11 and 13 , respectively, and a rear wall 15 .
- Refrigerator 10 also includes a closure door 16 for the refrigerator cabinet 12 which is hinged to cabinet 12 and a freezer door 18 hinged to the freezer cabinet 14 . Both doors 16 and 18 include suitable seals for providing an airtight thermally insulated sealed connection between the doors and respective cabinets.
- a side-by-side refrigerator/freezer is illustrated in FIG. 1 , the present invention can be employed with any configuration of a refrigerator/freezer combination.
- Refrigerator 10 is adapted to receive a variety of shelves and modules at different positions defined by, in the embodiment shown in FIG. 1 , a plurality of horizontally spaced vertical rails 22 extending from the rear wall of the refrigerator and freezer compartments.
- the supports are in the form of vertically extending rails with vertically spaced slots for receiving mounting tabs on shelf supports 23 and similar tabs on modules, such as modules 20 , 24 , 25 , and 26 , for attaching them in cantilevered fashion to the cabinets at selected incrementally located positions.
- the inside edges of doors 16 and 18 also include vertically spaced shelf supports, such as 27 , for positioning bins 29 and modules, such as 32 , in the doors.
- the shelves, modules, and bins and, thus, be located at a variety of selected locations within the cabinets 12 and 14 and doors 16 and 18 to allow the consumer to select different locations for convenience of use.
- module 20 may require operating utilities.
- module 20 may be a powered crisper or an instant thaw or chill module and may require utilities, such as cooled or heated fluids or electrical operating power.
- Other modules, such as module 26 may likewise require operational utilities while modules, such as a passive crisper module 20 , would not.
- Door modules also, such as module 32 may, for example, include a water dispenser, vacuum bag sealer or other accessory conveniently accessible either from the outside of door 16 or from within the door and likewise may receive operating utilities from conduits, such as disclosed in application Ser. Nos.
- Refrigerator 10 of this invention Contained within the insulated cabinets of the refrigerator are the usual freezer and fresh food evaporator, condenser, and the usual fluid couplings to a compressor for the operation of the refrigerator.
- Refrigerator 10 of this invention includes the improved condenser system of this invention, as shown in the schematic diagram of FIG. 2 , now described.
- the schematic diagram of FIG. 2 shows the locations of various major components of the refrigerator in no particular relationship within the refrigerator cabinet, it being understood that, in practice, these elements can be located in any conventional or convenient location.
- the condenser may conventionally be located in the back outside wall of the cabinet or in a compartment above cabinets 12 , 14 .
- the schematic diagram of FIG. 2 is illustrative only and does not necessarily limit the position of any of the components.
- refrigerator 10 includes a sealed compressor/pump unit 30 , which integrally includes a linear compressor 30 .
- compressor 30 Due to its relatively flat elongated shape, compressor 30 can be located conveniently at nearly any location within the refrigerator, including in the space between the refrigerator inner liner and its outer shell. Frequently, a compressor is located near the top of the refrigerator near the condenser where heat can be evacuated upwardly and away from the refrigerator cabinet.
- the compressor 30 can be of the type described in U.S. patent application Ser. No. 10/553,944 filed Apr. 22, 2004, entitled SYSTEM FOR ADJUSTING RESONANT FREQUENCIES IN A LINEAR COMPRESSOR and published as Publication No. 2006/0110259 on May 25, 2006. The disclosure of this application and publication are incorporated herein by reference.
- Compressor 30 is coupled to a refrigeration circuit 60 by an outlet/conduit 32 which couples the compressor to a condenser 40 of a first embodiment of the present invention and then to a two-way bypass valve 36 .
- a variable speed fan 42 is positioned adjacent condenser 40 to provide a cooling flow of ambient air across the condenser as described in greater detail below.
- the bypass valve 36 is selectively operated to either direct the refrigerant flow through a freezer compartment capillary 38 and into the freezer compartment evaporator 50 or via conduit 35 to the fresh food evaporator 70 through a thermostatic expansion valve 37 or other expansion device.
- a check valve 52 When in a position to direct refrigerant to the freezer evaporator 50 , a check valve 52 is open to the suction line 54 leading to the input 31 of the compressor. With the valve 36 in the freezer compartment bypass position, the refrigerant flows through conduit 35 into a thermostatic expansion valve 37 , into the fresh food evaporator 70 , and then into the suction line 54 again leading to the input 31 of compressor 30 .
- Bypass valve 36 is selectively operated by a microprocessor-based control circuit to either allow the flow of refrigerant through the freezer evaporator 50 or, alternatively, through the fresh food evaporator 70 depending upon the thermal demand of the compartments 14 , 12 , respectively.
- suction line 54 typically is in thermal communication with freezer capillary 38 or fresh food expansion device 37 for operational efficiency.
- the compressor 30 may include a hot gas bypass proportional valve 33 coupled between the input 31 and output 32 of compressor 30 to modulate the capacity of the compressor 40 as desired during different operational conditions.
- the refrigeration system described thus, includes a microprocessor-based control circuit with suitable temperature sensors which can be of a generally conventional design and operated in modes shown in the table of FIG. 10 .
- the refrigerator 10 includes a linear compressor 30 , in the preferred embodiment of the invention, which provides superior energy performance under normal operating conditions and excels in partial load conditions and has the characteristic of being more favorably responsive to condensing pressure, specifically, the lower condensing pressure results in an amplified increase in pumping capacity relative to power draw in comparison with similar nominal capacity reciprocating compressors.
- a linear compressor 30 in the preferred embodiment of the invention, which provides superior energy performance under normal operating conditions and excels in partial load conditions and has the characteristic of being more favorably responsive to condensing pressure, specifically, the lower condensing pressure results in an amplified increase in pumping capacity relative to power draw in comparison with similar nominal capacity reciprocating compressors.
- the improved condenser 40 configuration shown in detail in FIGS. 4 and 5 is employed.
- FIG. 1 the improved condenser 40 configuration shown in detail in FIGS. 4 and 5 is employed.
- the condenser 40 comprises a coaxial arrangement of an inner refrigerant tube 41 coaxially surrounded by a larger diameter tube 44 , between which there is inserted a phase change material 60 ( FIG. 5 ), such as paraffin wax having a specific heat capacity of from about 2.14-2.9 joules per gram per degree Kelvin and a heat fusion of 200-220 joules per gram.
- the solid phase change material melts at from about 85° F. to about 100° F. during the operation of compressor 30 transferring heat from the heated refrigerant in conduit 41 and, therefore, provides cooling to the condenser 40 and refrigerant therein with heat being continuously rejected to the ambient air via the cooling fins 46 of the condenser 40 .
- phase change material can be Glauber's salt (historically Sal Mirabilis), which has similar melting temperatures in the about 85° F. to about 100° F. range, or equivalent phase transition material, such as a variety of hydrated salts, a specific example being Thermal Salt LatestTM 29T.
- the outer tube 44 concentrically surrounds refrigerant tube 41 in which a refrigerant 62 flows in typically a heated gas and subsequently liquid form as it exits the condenser.
- the coaxial tubes 41 and 44 are supported by supports 46 and 48 at opposite ends and a plurality of parallel spaced conventional fins 46 , typically made of aluminum, are affixed to the outer diameter of tube 44 in a conventional manner to be in thermal communication with the tubes.
- the condenser 40 can be modified as illustrated in FIG. 6 to utilize straight sections 44 of sealed coaxial tubes surrounding refrigerant tube 41 within the body of condenser 40 .
- the inner refrigerant tubes 41 are curved at 49 ′, as seen in FIG. 6 , without the supplemental coaxial tubing 44 surrounding the curved sections extending from the ends of supports 46 and 48 .
- a sufficient number of sections 44 of coaxial conduits 41 and 44 are provided in the condenser to provide efficient cooling of the refrigerant prior to exiting the condenser.
- the use of a phase change material allows the continuous transfer of heat to the ambient during both compressor on and off operation, while the use of variable speed fan 42 assists in the transfer of heat from condenser and phase change material. This allows a reduced mass of refrigerant charge in the system, resulting in lowered off-cycle refrigerant migration losses.
- FIG. 7 An alternative embodiment of the invention is shown in FIG. 7 , in which a refrigeration circuit 60 is shown, including (for illustrative purposes only) a single evaporator, such as evaporator 70 , coupled to the suction line 54 of compressor 30 having an input 31 and output 32 leading to condenser 140 .
- Condenser 140 includes phase change material, such as sealed fin-like containers 144 (similar to radiation elements) in thermal communication with refrigerant-containing conduits 141 .
- the phase change material is the same as in the first embodiment and is in close thermal communication with the conduits 141 , so as to change phase from solid to liquid during an on cycle of compressor 30 and subsequently change back to the solid form during an off phase of operation.
- a variable speed condensing fan 142 is associated with condenser 140 for assisting in the transfer of heat from the condenser.
- a secondary coolant circuit 160 includes a condenser 150 of conventional construction including a coolant conduit 152 which extends through cooling fins 154 , which are cooled by a secondary condensing fan 156 .
- the coolant line or conduit 152 is filled with a suitable heat transfer media, such as a water/alcohol mixture or refrigerant so a thermosyphon heat transfer system is established with flow driven by density gradients or a heat pipe arrangement with flow driven by surface tension effects.
- Conduit 152 extends into condenser 140 and is in thermal communication with phase change elements 144 , as well as refrigerant conduit 141 , to transfer heat from condenser 140 to secondary condenser 150 by convection flow.
- This construction allows condenser 140 to be somewhat smaller than condenser 40 , if desired, and, with the secondary condenser 150 and pair of fans 142 and 156 , which can be operated either at a relatively low continuous speed or at a high (turbo mode) speed for efficiency, provides sufficient cooling of the refrigerant under abnormally high load conditions to allow the compressor 30 to efficiently operate.
- the secondary cooling circuit 160 serves as a thermal siphon to extract heat from the primary condenser 140 .
- the phase change material 144 in fin-like containers 145 can be extended to bridge both refrigerant condenser 140 and secondary coolant condenser 150 .
- a condenser employing a phase change material is essentially expelling heat 100% of the time to reduce the average condensing temperature and increase the energy efficiency of the refrigeration system.
- the heat rejection of the condenser improves during compressor run time when the refrigerant discharged from the compressor rejects heat to the phase change material which, in turn, transfers heat to the ambient air with the assistance of the variable speed fans.
- the concentric tube arrangement is one example of how such a condenser with phase change material can be constructed.
- phase change material rejects heat to the ambient air through natural convection or forced convection through the use of variable speed fans and efficiently transfers heat away from the refrigerant via a conduction pathway into the thermal absorber that undergoes a phase transition which, in turn, provides substantial thermal capacity at or near constant temperature leading to a refrigeration system with increased capacity resulting in shorter cooling cycles, faster pull down rates, and lower overall energy consumption.
- phase change material may not be necessary.
- the system is substantially the same as shown in FIG. 7 without the use of a phase change material 144 .
- the refrigerant circuit 60 employs a first condenser 140
- a second coolant circuit 160 includes a secondary condenser 150 , both of which are in thermal communication with adjacently positioned fans 142 and 156 , respectively.
- flammable refrigerants such as R-600a (Isobutane)
- FIG. 9 shows yet another embodiment of the invention in which a single condenser 140 of the same general construction as shown by condenser 140 in FIG. 7 is employed but without the use of a secondary condenser.
- phase change material is positioned again in fin-like holders 144 surrounded by and in thermal communication with the refrigerant conduit 141 of condenser 140 .
- a variable speed fan 142 is employed for cooling the condenser and the phase change material holders during high demand conditions where the compressor 30 is running and the condenser is being heated by the refrigerant.
- the same numerals employed with the same reference numerals and their operation are identical with that shown in FIG. 7 , however, fan 142 plays a somewhat more important role in providing an airflow through condenser 140 to maintain the condenser temperature relatively low during operation, thus, improving the efficiency of the compressor 30 and in resolidifying the phase change material during compressor off mode.
- FIG. 10 is a table showing the various modes of operation of the systems, including the on/off state of the compressor and fans during cycles of operation.
- the control circuit for the system will include a microprocessor programmed according to the refrigerator set temperatures as noted in the table of FIGS. 10A-10B and is programmed in a conventional manner to control the operation of the system as indicated by the table of FIGS. 10A-10B .
- FIG. 11 is a graph representing cycles of operation of a conventional condensing unit as compared to the improved high efficiency condensing unit of the present invention.
- Curves 90 and 92 illustrate the power, temperature, and on-time of a typical compressor employed with a normal condensing system.
- the phase change media (PCM) linear compressor 30 operation is represented by graphs 94 and 96 , which indicates the compressor power, temperature activation, on-time and temperature cycling.
- the power is slightly higher, but it operates for a shorter period of time than a system with a conventional condenser.
- Graph 96 represents the high efficiency condenser 40 operation, which, as can be seen, lowers the temperature significantly as compared to the graph 92 of a conventional condensing unit. This allows the compressor 30 to run a shorter period of time while providing a higher cooling capacity and, thus, faster temperature recovery for the refrigerated storage compartment during pull-down and normal cycling modes.
- a refrigeration system can operate to reach a given set point in a relatively shorter time frame to provide superior food preservation performance.
- the condenser system can be employed to improve the efficiency of operation of a refrigeration system utilizing a conventional reciprocating compressor.
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Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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US12/764,149 US20110259041A1 (en) | 2010-04-21 | 2010-04-21 | High efficiency condenser |
EP11158538A EP2381193A2 (fr) | 2010-04-21 | 2011-03-16 | Condensateur à haute efficacité |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US12/764,149 US20110259041A1 (en) | 2010-04-21 | 2010-04-21 | High efficiency condenser |
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US20110259041A1 true US20110259041A1 (en) | 2011-10-27 |
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US12/764,149 Abandoned US20110259041A1 (en) | 2010-04-21 | 2010-04-21 | High efficiency condenser |
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US (1) | US20110259041A1 (fr) |
EP (1) | EP2381193A2 (fr) |
Cited By (26)
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US20120000240A1 (en) * | 2010-07-01 | 2012-01-05 | Brent Alden Junge | Refrigerant cooling device |
US20120232936A1 (en) * | 2011-03-11 | 2012-09-13 | Castlight Health, Inc. | Reference Pricing of Health Care Deliverables |
US20120279245A1 (en) * | 2011-05-02 | 2012-11-08 | General Electric Company | Compact discharge device for the refrigeration compressor of an appliance |
US20130047652A1 (en) * | 2011-08-30 | 2013-02-28 | Taehee Lee | Refrigerator and control method thereof |
US20130160476A1 (en) * | 2011-12-21 | 2013-06-27 | Sangbong Lee | Refrigerator |
US8893513B2 (en) | 2012-05-07 | 2014-11-25 | Phononic Device, Inc. | Thermoelectric heat exchanger component including protective heat spreading lid and optimal thermal interface resistance |
US8991194B2 (en) | 2012-05-07 | 2015-03-31 | Phononic Devices, Inc. | Parallel thermoelectric heat exchange systems |
US9016070B2 (en) | 2012-09-14 | 2015-04-28 | Whirlpool Corporation | Phase change materials for refrigeration and ice making |
WO2015087229A1 (fr) * | 2013-12-09 | 2015-06-18 | BSH Hausgeräte GmbH | Condensateur, procédé de fabrication d'un condensateur et appareil de refroidissement équipé du condenseur |
WO2015148346A1 (fr) * | 2014-03-24 | 2015-10-01 | The Coca-Cola Company | Système de réfrigération avec échangeur de chaleur à matériau à changement de phase |
US20160201931A1 (en) * | 2013-08-29 | 2016-07-14 | Carrier Corporation | Thermal energy storage assembly with phase change materials |
DE102015105064A1 (de) * | 2015-04-01 | 2016-10-06 | Solfridge GmbH & Co. KG | Speicherkühlgerät in selbsttragender Bauweise |
US9593871B2 (en) | 2014-07-21 | 2017-03-14 | Phononic Devices, Inc. | Systems and methods for operating a thermoelectric module to increase efficiency |
US20170227272A1 (en) * | 2016-02-04 | 2017-08-10 | Lg Electronics Inc. | Air conditioner and method of controlling the same |
US20170363363A1 (en) * | 2016-06-21 | 2017-12-21 | Ge Aviation Systems Llc | Electronics Cooling with Multi-Phase Heat Exchange and Heat Spreader |
CN108496052A (zh) * | 2016-01-29 | 2018-09-04 | 松下知识产权经营株式会社 | 冷藏库 |
US10458683B2 (en) | 2014-07-21 | 2019-10-29 | Phononic, Inc. | Systems and methods for mitigating heat rejection limitations of a thermoelectric module |
US11199354B2 (en) * | 2017-05-02 | 2021-12-14 | Viessmann Werke Gmbh & Co. Kg | Refrigeration unit having an accumulator, refrigeration system and method for controlling a refrigeration unit having an accumulator |
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US11745847B2 (en) | 2020-12-08 | 2023-09-05 | General Electric Company | System and method for cooling a leading edge of a high speed vehicle |
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GB2484752B (en) * | 2010-10-23 | 2016-05-11 | Ebac Ltd | Condenser cooling in refrigeration circuits |
WO2016013798A1 (fr) | 2014-07-21 | 2016-01-28 | Lg Electronics Inc. | Réfrigérateur et procédé de commande dudit réfrigérateur |
CN105135748B (zh) * | 2015-08-20 | 2018-03-06 | 杭州雪中炭恒温技术有限公司 | 恒温换热机构 |
TR201612430A2 (tr) * | 2016-09-02 | 2018-03-21 | Arcelik As | Portati̇f i̇kli̇mlendi̇rme ci̇hazi |
CN112352134A (zh) * | 2018-07-11 | 2021-02-09 | 林德有限责任公司 | 温度补偿元件、管和用于制造管的方法 |
FR3090081B1 (fr) * | 2018-12-13 | 2021-02-26 | Commissariat Energie Atomique | Système de production de froid comprenant une machine à compression, une machine à absorption et un système de stockage thermique assurant leur couplage |
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DE102015105064B4 (de) * | 2015-04-01 | 2021-03-18 | Solfridge GmbH & Co. KG | Speicherkühlgerät in selbsttragender Bauweise und Verfahren zum Betrieb eines Speicherkühlgeräts |
CN108496052A (zh) * | 2016-01-29 | 2018-09-04 | 松下知识产权经营株式会社 | 冷藏库 |
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US11260976B2 (en) | 2019-11-15 | 2022-03-01 | General Electric Company | System for reducing thermal stresses in a leading edge of a high speed vehicle |
US11260953B2 (en) | 2019-11-15 | 2022-03-01 | General Electric Company | System and method for cooling a leading edge of a high speed vehicle |
US11267551B2 (en) | 2019-11-15 | 2022-03-08 | General Electric Company | System and method for cooling a leading edge of a high speed vehicle |
US11352120B2 (en) | 2019-11-15 | 2022-06-07 | General Electric Company | System and method for cooling a leading edge of a high speed vehicle |
US11427330B2 (en) | 2019-11-15 | 2022-08-30 | General Electric Company | System and method for cooling a leading edge of a high speed vehicle |
US11745847B2 (en) | 2020-12-08 | 2023-09-05 | General Electric Company | System and method for cooling a leading edge of a high speed vehicle |
US11407488B2 (en) | 2020-12-14 | 2022-08-09 | General Electric Company | System and method for cooling a leading edge of a high speed vehicle |
US11577817B2 (en) | 2021-02-11 | 2023-02-14 | General Electric Company | System and method for cooling a leading edge of a high speed vehicle |
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