CA2394474A1 - Refrigeration units and heat pipe - Google Patents
Refrigeration units and heat pipe Download PDFInfo
- Publication number
- CA2394474A1 CA2394474A1 CA002394474A CA2394474A CA2394474A1 CA 2394474 A1 CA2394474 A1 CA 2394474A1 CA 002394474 A CA002394474 A CA 002394474A CA 2394474 A CA2394474 A CA 2394474A CA 2394474 A1 CA2394474 A1 CA 2394474A1
- Authority
- CA
- Canada
- Prior art keywords
- thermoelectric modules
- manifold
- cooling
- heat pipes
- thermal communication
- 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.)
- Abandoned
Links
Classifications
-
- 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
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/0266—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
- F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
- F24F12/002—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0042—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater characterised by the application of thermo-electric units or the Peltier effect
-
- 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
- F25B21/00—Machines, plants or systems, using electric or magnetic effects
- F25B21/02—Machines, plants or systems, using electric or magnetic effects using Peltier effect; using Nernst-Ettinghausen effect
-
- 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
- F25B21/00—Machines, plants or systems, using electric or magnetic effects
- F25B21/02—Machines, plants or systems, using electric or magnetic effects using Peltier effect; using Nernst-Ettinghausen effect
- F25B21/04—Machines, plants or systems, using electric or magnetic effects using Peltier effect; using Nernst-Ettinghausen effect reversible
-
- 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
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/0233—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes the conduits having a particular shape, e.g. non-circular cross-section, annular
-
- 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
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/0275—Arrangements for coupling heat-pipes together or with other structures, e.g. with base blocks; Heat pipe cores
-
- 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
- F25B2321/00—Details of machines, plants or systems, using electric or magnetic effects
- F25B2321/02—Details of machines, plants or systems, using electric or magnetic effects using Peltier effects; using Nernst-Ettinghausen effects
- F25B2321/025—Removal of heat
- F25B2321/0251—Removal of heat by a gas
-
- 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
- F25B2321/00—Details of machines, plants or systems, using electric or magnetic effects
- F25B2321/02—Details of machines, plants or systems, using electric or magnetic effects using Peltier effects; using Nernst-Ettinghausen effects
- F25B2321/025—Removal of heat
- F25B2321/0252—Removal of heat by liquids or two-phase fluids
-
- 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
- F25D2400/00—General features of, or devices for refrigerators, cold rooms, ice-boxes, or for cooling or freezing apparatus not covered by any other subclass
- F25D2400/12—Portable refrigerators
-
- 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]
- Y02B30/56—Heat recovery units
Abstract
A refrigerator includes a housing that defines an enclosable storage space.
The refrigerator includes a closed manifold which defines a chamber to contain refrigerant. The chamber is made up of three parts, a cooling pipe, a head pipe, and one or more heat pipes to communicate fluid between the cooling and head pipes. The heat pipes are flat, elongated, and are divided internally to form capillary channels to permit flow of refrigerant between the cooling and head pipes. An array of thermoelectric modules contacts a surface of the manifold to chill refrigerant within the manifold. A pump or compressor is not required to circulate the refrigerant within the system. A blower forces an air stream to cool the heating faces of the thermoelectric modules. A control unit may be used to maintain the operating temperature of the refrigerator. A refrigerator may be portable, with a portable power source or adapters. The manifold design is useful for modular refrigerator appliance designs. The manifold is also useful in other refrigerating systems, cold storage units and portable devices.
The refrigerator includes a closed manifold which defines a chamber to contain refrigerant. The chamber is made up of three parts, a cooling pipe, a head pipe, and one or more heat pipes to communicate fluid between the cooling and head pipes. The heat pipes are flat, elongated, and are divided internally to form capillary channels to permit flow of refrigerant between the cooling and head pipes. An array of thermoelectric modules contacts a surface of the manifold to chill refrigerant within the manifold. A pump or compressor is not required to circulate the refrigerant within the system. A blower forces an air stream to cool the heating faces of the thermoelectric modules. A control unit may be used to maintain the operating temperature of the refrigerator. A refrigerator may be portable, with a portable power source or adapters. The manifold design is useful for modular refrigerator appliance designs. The manifold is also useful in other refrigerating systems, cold storage units and portable devices.
Description
REFRIGERATION UNITS AND HEAT PIPE
BACKGROUND OF THE INVENTION
Field of the Invention The present invention relates to refrigeration units, including refrigerator s appliances, refrigerating systems, and cold storage units.
Background Many earlier refrigeration systems have utilized refrigerants that are potentially harmful when released to the environment. Certain refrigerants are desirable because they present higher operating efficiencies when used in conventional to systems, although they may pose adverse environmental risks. Some efforts have been made to replace such harmful gaseous fluids with alternative fluids that are less harmful to the environment. However, such systems have suffered from various limitations and relatively low heat transfer efficiencies.
In addition, earlier cooling and heating systems have included conventional heat is exchange manifolds, piping and pumping systems for refrigerants. Some of the earlier systems have also incorporated thermoelectric modules for specifically defined cooling or heating functions. By way of example, the following US
Patents described examples of such earlier systems: US Patent 6,354,086 to Inoue et al., US Patent 5,232,516 to Hed, US Patent 5,269,146 to Kerner, US
zo Patent 5,540,567 to Schirpke et al., US Patent 5,653,111 to Attey et al., and US
Patent 5,675,973 to Dong. The foregoing examples describe conventional fluid pumping and piping systems for transportation of fluid within the heat transfer or cooling systems described in those patents.
Some of the earlier systems have attempted to improve the efficiency of heat exchange by incorporating complex fluid agitators. US Patent 6,354,086 to Inoue et al. is an example of an earlier patent in which such agitators are described.
US Patent 5,269,146 describes a closed system heating and cooling system for thermally insulated containers such as portable refrigerated chests, heated bottles and serving carts for hotels and restaurants. Thermally conductive fluid is circulated through a closed loop circulating system. The heated or cooled fluid is io passed through an air core heat exchanger for heat exchange with surrounding ambient air. The patent describes that the fluid is pumped at high speeds through the closed system to promote efficient heat transfer.
Korean patent 2000-54406 is an example of an earlier cooling system using a thermoelectric module and conventional heat transfer arrangement. Another is example of an earlier heat transfer system employing a heat transfer pipe without thermoelectric module components, is described in Korean patent number 190443. All of these earlier systems include conventional piping and circulation systems for refrigerants or other fluids. Many of these systems are prone to leakage and system malfunctions associated with mechanical problems, such as 2o compressor failures.
These earlier systems have not addressed the advantages of providing refrigeration systems having the improved efficiencies associated with the use of natural forces and inherent fluid flow characteristics of the capillary flow systems described below.
SUMMARY OF THE INVENTION
The invention includes a refrigeration apparatus. In one aspect, the manifold defines an inner chamber containing an effective amount of a selected refrigerant. The inner chamber comprises an elongated first chamber, an elongated second chamber, and a plurality of heat pipes which define capillary channels in fluid communication between the first and second chambers. A
selected number of thermoelectric modules are used to cool the refrigerant io contained within the manifold. Preferably, the thermoelectric modules are positioned in cooling contact with a thermal transfer area defined by the manifold.
A blower is provided to remove excess heat from the heating faces of the thermoelectric modules.
Thermoelectric modules are also known in the art as Pettier devices. Earlier is examples of Pettier devices are generally wafer-like structures that produce heat and cooling effects upon application of electric current.
In another aspect, a refrigeration device is provided. In this example, the refrigeration device includes a housing. The housing defines one or more interior spaces. The interior spaces are in cooling, thermal communication with one or 2o more manifolds. Each manifold defines an interior chamber containing an effective amount of a selected refrigerant. The inner chamber of the manifold comprises:
a first cylinder, a second cylinder, and a plurality of capillary channels defined by the heat pipes. The channels establish fluid communication between the first and second cylinders. A plurality of thermoelectric modules are arranged so that their cooling faces thermally communicate with the manifold.
In this example, one or more blowers are provided to force an air stream to cool the heating faces of the thermoelectric modules.
By way of example, in another aspect, the present invention includes a heat transfer manifold used with arranged banks of thermoelectric modules. The io apparatus may be employed in association with refrigeration systems, including appliances, cold storage units and other cooling systems. The manifold is particularly useful in those instances where it is desirable to avoid the use of conventional refrigerants such as freon and other potentially harmful refrigerants.
Examples of preferred refrigerants are described.
is The manifold is typically positioned in a generally vertical orientation when the manifold is in operation, as described in more detail further below. In one aspect, the manifold comprises an upper cooling pipe that is in parallel alignment with a vertically opposed feeder pipe or head pipe. The head pipe or cooling pipe may be provided with a fluid opening to input thermally conductive fluid. In some 2o instances, the fluid opening may be resealable so that refrigerant may be re-charged into the manifold. A plurality of generally planar heat pipes are positioned between the cooling pipe and the head pipe. In some instances, it is desirable to position the heat pipes so that their planar faces are parallel to the longitudinal axes of the cooling pipe and head pipe. In this embodiment, the heat pipes are coplanar and positioned so that their planar faces are aligned along the lengths of the cooling pipe and head pipe.
As noted above, a refrigerant is provided within the closed fluid reservoir of the manifold. Heat exchange occurs through the operation of the thermoelectric modules and the repeated evaporation and condensation of the refrigerant within the fluid reservoir of the manifold.
Preferably, each heat pipe is generally elongated and flat. The heat pipe is io internally divided into capillary channels running along the length of the heat pipe.
Preferably, the channels form a single layer of capillaries running along the length of the heat pipe. Each capillary channel extends from one end of the heat pipe to the other end of the heat pipe. Each capillary channel provides fluid communication between the cooling pipe and the opposed head pipe.
is The manifold component may be used in combination with a plurality of thermoelectric modules that have been aligned in planar arrays so that all heating faces of the modules are along one side of the array, and the cooling faces of the modules are along the opposite side of the array. The row of modules is positioned adjacent to the manifold to establish cooling, thermal communication 2o between the cooling faces of the modules and the manifold.
In some instances, the row of thermoelectric modules may be placed in contact with a heat transfer surface defined by either the cooling pipe, head pipe, or a coplanar array of heat pipes. In the preferred embodiment, the cooling faces of the thermoelectric modules are placed in thermal communication with an elongated heat transfer surface defined by the cooling pipe.
In one aspect of the invention, the capillary channels in a heat pipe are generally rectangular tubes defined by the interior walls of the heat pipe. Preferably, the interior walls extend orthogonally from one face of the heat pipe to the opposing face of the heat pipe. However, the capillaries may be manufactured to have other cross-sectional configurations that are not necessarily square or rectangular in shape. The relative size of the capillaries will vary according to the 1o design requirements and characteristics of the desired cooling system. The diameter of the capillaries may be adjusted to accommodate the particular flow characteristics of a specific fluid selected for use in the system. Design characteristics, including the optimal diameters for the capillaries may be adapted to account for differences in fluid flow, heat transfer characteristics, surface is tension, and other physical properties exhibited by different refrigerants.
In a preferred embodiment, the manifold will be positioned for operation so that the capillaries will extend in a generally vertical direction. The fluid flow and heat transfer characteristics within the capillaries will be enhanced by this vertical arrangement. It is preferred that the rows of modules be positioned near the top 20 of the manifold to enhance generally downward thermal and fluid flow tendencies within the capillaries.
In a preferred embodiment, the capillaries are arranged in a single layer of capillaries within the outer walls of the heat pipes. In other instances, multiple layers of capillaries may be provided within the outer walls of a heat pipe, although in many cases, such an arrangement may not be preferred.
The manifold component is preferably made of a relatively strong, resilient, and thermally conductive material and most preferably, a metal which is not susceptible to excessive corrosion. Aluminum is a particularly useful material of construction for many applications of the present invention. Of course, persons skilled in the art will understand that other materials, including other metals, io alloys, or non metallic materials may be desirable for use in the particular conditions and circumstances under consideration.
Preferably, the fluid within the reservoir is filled until the liquid phase occupies about 40% to 70% of the volume of the reservoir. The vapor phase will occupy between about 30% and 60% of the volume of the reservoir. In a preferred is cooling application, a suitable coolant will be filled until about 60% -70% of the reservoir volume is filled with the liquid phase, and 30% - 40% of that volume is filled with the vapor phase.
Embodiments of the inventions may be made of modular components, unlike many conventional cooling system designs. For example, the cooling manifolds 2o are self contained units, and once they are disconnected from a power source, and optional control unit, may be extracted from the enclosing structure. The removed manifold or other modular components may be repaired or replaced with relative ease. Many conventional systems have complicated piping and pumping systems, expensive components and present various obstacles to repair or replacement of the refrigerating cores. Conventional pumps, compressors, and other system components are often expensive. The invention s includes embodiments which permit system designs avoiding the use of many expense conventional system components.
Other embodiments of the invention include fixed cold storage compartments provided in buildings and other structures. By way of example, modular manifold arrangements may be provided for installation along one or more interior walls of io an insulated cold storage compartment of a building. In other embodiments, refrigerator units may be manufactured for installation with storage compartments and vehicles, including truck trailers, shipping containers and other like structures.
BRIEF DESCRIPTION OF THE DRAWINGS
is In the following description, the invention is further explained in connection with a preferred embodiment making reference to the drawings in which:
Fig. 1 is a perspective, exploded representation of a refrigerator appliance in which the major components are depicted in a disassembled view.
Fig. 2 is a perspective representation of a cooling manifold wherein the major 2o comments are depicted in an exploded view.
Fig. 3 is a perspective depiction of an enlarged partial exploded view of a heat pipes and cooling pipe of the manrfold depicted in Fig. 2.
Fig. 4 is an enlarged partial view of two adjacent heat pipes depicted in Fig.
3.
Fig. 5 is an enlarged partial sectional view of several adjacent heat pipes of the s manifold and the head pipe portion the manifold shown in Fig. 2.
Fig. 6 is a perspective depiction of a partial section of an upper portion of the manifold shown in Fig. 2.
Fig. 7 is a perspective depiction of a partial section of an upper portion of the manifold shown in Fig. 2, further depicting an array of cooling fins adjacent the io upper portion of the manifold.
Fig. 8 is a perspective depiction of the air cooling components of the manifold shown in Fig. 2, depicted in exploded view.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Fig. 1 shows a refrigerator appliance as one embodiment of the present invention is in an exploded view, featuring several major components of the refrigerator.
Outer doors 100 enclose two interior compartments defined by a unitary shell 200. A cooling manifold assembly 300 includes two manifold assemblies which surround opposing side walls of shell 200. An outer housing 500 is provided to receive the other major components of the refrigerator appliance. Upper hinge mounts 510 and lower hinge mounts 520 are used to secure front doors 100 to the housing 500.
In Fig. 1, one of the two manifold assemblies is depicted in exploded view.
The manifold assembly 300 includes two opposing banks of heat pipes 320. The two banks of heat pipes are depicted in a generally, vertical arrangement. The two banks of heat pipes, when installed in the appliance, will be in thermal communication with a corresponding internal storage compartment of the appliance. The two banks of heat pipes are preferably parallel to the interior walls of the storage compartment. Each bank of heat pipes 320 is attached for to fluid communication with a corresponding head pipe 330. Refrigerant is charged within the interior chamber of the manifold. The refrigerant circulates without the use of a refrigerant pump or compressor. Each bank of heat pipes presents a substantial heat transfer area, due in part to the elongated, flat surfaces of the heat pipes. Similarly, the internal capillary structure of the heat pipes further is enhances the effective heat transfer area between the refrigerant and the interior space of the storage compartment. The substantial heat transfer area enhances the overall efficiency of the refrigeration system.
An upper cooling assembly 310 comprises a linear array of cooling fans, positioned in thermal communication above an array of thermoelectric modules 20 315 and an underlying cooling pipe 317. Fig. 3 shows an enlarged partial view of the connection established between upper ends of heat pipes 320 and corresponding fluid ports leading to the interior chamber defined by cooling pipe 317. Cooling pipe 317, in this embodiment, provides a common chamber for n circulating refrigerant contained within the manifold. The heat pipes of both opposing banks of heat pipes are in common, fluid communication with the interior chamber of the cooling pipe 317. Refrigerant contained within the manifold communicates between the interior space defined by the cooling pipe s 317 and the head pipes 330. Each head pipe 330 defines an interior space for fluid communication between the opposite (lower) ends of the respective banks of heat pipes 320. Refrigerant contained within the manifold communicates between head pipes 330 and the cooling pipe 317 via the capillary channels defined in each heat pipe. Fig. 4 shows a pair of adjacent ends of heat pipes 1o 320, arranged in a common plane, with each heat pipe having a single layer of capillary channels extending in parallel along the length of the corresponding heat pipe. The capillary channels in the heat pipes allow refrigerant to communicate between head pipes 330 and the common cooling pipe 317. With reference with Fig. 5, downwardly oriented arrows represent chilled refrigerant is traveling downwardly along the various capillary channels. Chilled refrigerant, travelling in plugs of condensed refrigerant liquid, descends along the capillary channels. At the same time, portions of the refrigerant will evaporate during operation of the manifold causing vapor plugs of the refrigerant to ascend through various capillary channels of the heat pipes (as represented by the 2o upwardly pointing arrow). Evaporated refrigerant enters into the cooling pipe 317 where the refrigerant will be chilled by the cooling operation of an array of thermoelectric modules 315.
With reference to Figs. 6, 7, and 8, a linear array of thermoelectric modules contacts a heat transfer surface defined by cooling pipe 317. The thermoelectric modules 315 are all arranged so that their respective cooling faces are in contact with cooling pipe 317. Consequently, the heating faces of the thermoelectric modules 315 face outwardly away from the cooling pipe 317. The heating faces of the thermoelectric modules 315 are in thermal communication with an upwardly projecting bank of cooling fins 314. Cooling fins 314 are arranged in parallel so that adjacent fins within the arrangement define air flow channels for air forced through the channels by a linear array of fans 312. The fans force air to across the cooling fins to remove excess heat generated by the heating faces of the thermoelectric modules 315. The fans are operated, preferably, through a control unit (not shown) set to activate the fans during operation of the thermoelectric modules 315. Similarly, the control panel (not shown) may be set to actively operate the thermoelectric modules to maintain a set, desirable is temperature for the internal storage compartment of the refrigerator appliance.
In Fig. 8, a detailed representation of the air cooling assembly is shown. As noted above, cooling pipe 317 defines a contact surface for the cooling faces of the array of thermoelectric module 315. Cooling pipe 317 includes a capped port 318 that may be used to charge and refill the manifold with a selected refrigerant.
2o The cooling assembly includes a protective gasket 316 which frames an array of thermoelectric modules 315. The gasket 316 is positioned between the lower surface of the cooling fin array 314 and the heat transfer surface defined by the cooling pipe 317. Gasket 316 protects the thermoelectric modules against accidental damage due to over tightening of the fasteners used to assemble the various components of the air cooling assembly. In addition, the gasket 316 may be provided with insulative qualities to inhibit undesirable heat transfer activity at the interface between the cooling fin array 314 and cooling pipe 317. The cooling pipe 317, the gasket 316, and the base of the cooling fin array 314 define co-axial holes for receiving bolts 311 used to secure the vertically stacked components of the cooling assembly. By way of example, bolt 311 extends through a co-axial bore defined by a fan housing in fan array 312, a bore defined by a support collar 313, the base of cooling fin array 314, a bore defined by to gasket 316, and a bore defined by cooling pipe 317. The bolts 311 are secured within the assembly by nuts (not shown).
In this embodiment, air is inducted into the air flow channels formed between opposing pairs of cooling fins 314. The flowing air is warmed upon contact with the cooling fins 314 and is exhausted near the upper end of the outer housing of is the refrigerator appliance. The heating faces of thermoelectric modules are thereby cooled to prevent overheating during operation of the refrigerator appliance.
In this illustrated embodiment, the interior compartment of the appliance includes a freezer compartment and cooling compartment. The freezer and cooling 2o compartments are arranged side by side. Two banks of heat pipes 320 i.e.
one bank from the two depicted manifolds, extend vertically through the gap formed between the freezer and chilling compartments. The first manifold, used to chill the cooling compartment, may be operated by a control panel which is separate and distinct from a second control panel used to operate the freezer compartment. The two control panels may be operated and wired independently of each other.
In the preferred embodiment, the cooling fans are arranged in two linear arrays, s in which one array of fans is positioned above the cooling manifold for the freezer compartment and a second fan array is positioned above the manifold used to cool the cooling compartment. The two cooling fan arrays are controlled independently in the preferred embodiment.
Although a refrigerator appliance is depicted in the preferred embodiment, other io embodiments will be apparent. For example, a portable cooling chest may be provided in which a manifold is used for cooling one or more interior walls of the chest. The overall size, configuration and power demands of the manifold are in part, depend upon the surface area, volume, and insulative qualities of the portable cooling chest. (A cooling chest may be designed for optimal operation is so that the chest is positioned, in its normal orientation, so that the heat pipes in the manifold define capillary channels orientated in a generally vertical direction.
In a portable cooling chest, a portable power source, including, a storage battery or portable generator may be provided to power a pre-selected number of thermoelectric modules to cool the internal compartment of the chest. One or 2o more cooling fans may be provided, as required. A cooling chest may also be provided with adapters to convert AC power to a DC power supply for the thermoelectric modules. Similarly, adapters may be provided to connect with is power outlets in vehicles for powering accessories. Other power source arrangements may also be provided.
The thermoelectric modules are supplied with electric current from a suitable power source which is not shown. The power source is typically a DC power unit s selected with the appropriate operational requirements for the thermoelectric modules and heat transfer requirements for the particular application.
A wide range of refrigerants may be used in the manifold of the invention, including conventional refrigerants. However, the following are two examples of preferred refrigerants, identified as OS-12bT"" and OS-12aT"", which are believed 1o to offer certain environmental advantages, as compared to selected conventional refrigerants.
Table 1 1) OS-l2bTM
Classification OS-12b HCFC-22 HFC-1 Molecular mass 113.38 120.93 102.03 Boiling temperature( -26.59 -29.8 -26.5 C) Heat of vaporization 248.3 149.8 198.7 at 0 C(KJ/Kg) Stabilities Thermal Stable Stable Stable Chemical Stable Stable Stable Erosive No No No Flammability(LFL None None None & UFL) Autoignition temperature( C) None None None Toxicity No No No O.D.P.(Ozone depletion potential) 0 1 0 G.W.P.(Global warming potential <3 8,100 1,300 in relation to C02 with 100 years integration time) Lubricant Mineral Mineral Ester 2) OS-l2aTM
Classification OS-12a HCFC-22 HFC-1 Molecular mass 57.9 120.93 102.03 Boiling temperature( -34.5 -29.8 -26.5 C) Heat of vaporization 367.0 149.8 198.7 at 0 C(KJ/Kg) Stabilities Thermal Stable Stable Stable Chemical Stable Stable Stable Erosive No No No Flammability(LFL 3.7-9.5% None None & UFL) Autoignition temperature( 540 None None C) Toxicity No No No O.D.P.(Ozone depletion 0 1 0 potential) G.W.P.(Global warming 3 8,100 1,300 potential in relation to C02 with 100 years integration time) Lubricant Mineral/EsterMineral Ester 4 , The above Table 1 is reproduced from information published by Technochem CO., Ltd. (htt~//www.technochem.com), Republic of Korea.
TM _ Trade-mark of Technochem Co., Ltd., Republic of Korea Of course, other refrigerants may be selected for various reasons. After a s suitable refrigerant is selected, it is preferable to evacuate entrapped air from the interior of the manifold, during manufacture of the manifold. For example, the air may be evacuated through an access port. In the preferred embodiment, substantially all of the entrapped air will be removed and thereafter, the refrigerant will be charged into the interior of the reservoir of the manifold.
io Certain other refrigerants will also be preferred for certain applications.
For example, conventional refrigerants such as R-142, R-141 B and others may be used in cooling applications with a suitably adapted heat exchange manifold.
With respect to the heat pipe design, it is believed that capillaries with cross-sectional diameters of about 4 mm in diameter were particularly efficient in is refrigeration applications. In some instances, it may be desirable to use capillaries with smaller effective diameters. Capillary tubes that are generally rectangular when viewed in cross section may have dimensions of 1 mm X 1.4 mm or lower. In other instances, the capillaries may have cross-sectional dimensions of about 0.5 mm X 0.6 mm. Of course, other sizes of capillaries may Zo be selected, based on various design considerations.
i8 However, the optimal size of the capillaries may vary according to the physical properties of the thermally conductive fluid selected for use in a particular heat exchange system. For example, surface tension, fluid viscosity and other factors may affect the optimal effective diameter of the capillaries in a particular system.
A number of factors may affect fluid performance and thus affect the optimal and maximum diameters of the capillaries to be provided in the refrigeration system.
It will be appreciated that refrigerants will tend to flow within the internal channels of the manifold due in part to cooling of the fluid and the capillary action exerted on the fluid within the capillaries of the manifold. One of the advantages of the io invention is that it is unnecessary to provide a circulating pump to circulate the refrigerant within the interior chamber of the manifold. Although there may be instances where a circulating pump may be added, such a pump would not be necessary to circulate the refrigerant provided within the manifold.
The present invention has been described with reference to preferred is embodiments. However, other embodiments of the invention, and variations and modifications thereof will be apparent to those persons having ordinary skill in the art. It is intended that those other embodiments, variations and modifications thereof, will be included within the scope of the present invention as claimed within the appended claims.
BACKGROUND OF THE INVENTION
Field of the Invention The present invention relates to refrigeration units, including refrigerator s appliances, refrigerating systems, and cold storage units.
Background Many earlier refrigeration systems have utilized refrigerants that are potentially harmful when released to the environment. Certain refrigerants are desirable because they present higher operating efficiencies when used in conventional to systems, although they may pose adverse environmental risks. Some efforts have been made to replace such harmful gaseous fluids with alternative fluids that are less harmful to the environment. However, such systems have suffered from various limitations and relatively low heat transfer efficiencies.
In addition, earlier cooling and heating systems have included conventional heat is exchange manifolds, piping and pumping systems for refrigerants. Some of the earlier systems have also incorporated thermoelectric modules for specifically defined cooling or heating functions. By way of example, the following US
Patents described examples of such earlier systems: US Patent 6,354,086 to Inoue et al., US Patent 5,232,516 to Hed, US Patent 5,269,146 to Kerner, US
zo Patent 5,540,567 to Schirpke et al., US Patent 5,653,111 to Attey et al., and US
Patent 5,675,973 to Dong. The foregoing examples describe conventional fluid pumping and piping systems for transportation of fluid within the heat transfer or cooling systems described in those patents.
Some of the earlier systems have attempted to improve the efficiency of heat exchange by incorporating complex fluid agitators. US Patent 6,354,086 to Inoue et al. is an example of an earlier patent in which such agitators are described.
US Patent 5,269,146 describes a closed system heating and cooling system for thermally insulated containers such as portable refrigerated chests, heated bottles and serving carts for hotels and restaurants. Thermally conductive fluid is circulated through a closed loop circulating system. The heated or cooled fluid is io passed through an air core heat exchanger for heat exchange with surrounding ambient air. The patent describes that the fluid is pumped at high speeds through the closed system to promote efficient heat transfer.
Korean patent 2000-54406 is an example of an earlier cooling system using a thermoelectric module and conventional heat transfer arrangement. Another is example of an earlier heat transfer system employing a heat transfer pipe without thermoelectric module components, is described in Korean patent number 190443. All of these earlier systems include conventional piping and circulation systems for refrigerants or other fluids. Many of these systems are prone to leakage and system malfunctions associated with mechanical problems, such as 2o compressor failures.
These earlier systems have not addressed the advantages of providing refrigeration systems having the improved efficiencies associated with the use of natural forces and inherent fluid flow characteristics of the capillary flow systems described below.
SUMMARY OF THE INVENTION
The invention includes a refrigeration apparatus. In one aspect, the manifold defines an inner chamber containing an effective amount of a selected refrigerant. The inner chamber comprises an elongated first chamber, an elongated second chamber, and a plurality of heat pipes which define capillary channels in fluid communication between the first and second chambers. A
selected number of thermoelectric modules are used to cool the refrigerant io contained within the manifold. Preferably, the thermoelectric modules are positioned in cooling contact with a thermal transfer area defined by the manifold.
A blower is provided to remove excess heat from the heating faces of the thermoelectric modules.
Thermoelectric modules are also known in the art as Pettier devices. Earlier is examples of Pettier devices are generally wafer-like structures that produce heat and cooling effects upon application of electric current.
In another aspect, a refrigeration device is provided. In this example, the refrigeration device includes a housing. The housing defines one or more interior spaces. The interior spaces are in cooling, thermal communication with one or 2o more manifolds. Each manifold defines an interior chamber containing an effective amount of a selected refrigerant. The inner chamber of the manifold comprises:
a first cylinder, a second cylinder, and a plurality of capillary channels defined by the heat pipes. The channels establish fluid communication between the first and second cylinders. A plurality of thermoelectric modules are arranged so that their cooling faces thermally communicate with the manifold.
In this example, one or more blowers are provided to force an air stream to cool the heating faces of the thermoelectric modules.
By way of example, in another aspect, the present invention includes a heat transfer manifold used with arranged banks of thermoelectric modules. The io apparatus may be employed in association with refrigeration systems, including appliances, cold storage units and other cooling systems. The manifold is particularly useful in those instances where it is desirable to avoid the use of conventional refrigerants such as freon and other potentially harmful refrigerants.
Examples of preferred refrigerants are described.
is The manifold is typically positioned in a generally vertical orientation when the manifold is in operation, as described in more detail further below. In one aspect, the manifold comprises an upper cooling pipe that is in parallel alignment with a vertically opposed feeder pipe or head pipe. The head pipe or cooling pipe may be provided with a fluid opening to input thermally conductive fluid. In some 2o instances, the fluid opening may be resealable so that refrigerant may be re-charged into the manifold. A plurality of generally planar heat pipes are positioned between the cooling pipe and the head pipe. In some instances, it is desirable to position the heat pipes so that their planar faces are parallel to the longitudinal axes of the cooling pipe and head pipe. In this embodiment, the heat pipes are coplanar and positioned so that their planar faces are aligned along the lengths of the cooling pipe and head pipe.
As noted above, a refrigerant is provided within the closed fluid reservoir of the manifold. Heat exchange occurs through the operation of the thermoelectric modules and the repeated evaporation and condensation of the refrigerant within the fluid reservoir of the manifold.
Preferably, each heat pipe is generally elongated and flat. The heat pipe is io internally divided into capillary channels running along the length of the heat pipe.
Preferably, the channels form a single layer of capillaries running along the length of the heat pipe. Each capillary channel extends from one end of the heat pipe to the other end of the heat pipe. Each capillary channel provides fluid communication between the cooling pipe and the opposed head pipe.
is The manifold component may be used in combination with a plurality of thermoelectric modules that have been aligned in planar arrays so that all heating faces of the modules are along one side of the array, and the cooling faces of the modules are along the opposite side of the array. The row of modules is positioned adjacent to the manifold to establish cooling, thermal communication 2o between the cooling faces of the modules and the manifold.
In some instances, the row of thermoelectric modules may be placed in contact with a heat transfer surface defined by either the cooling pipe, head pipe, or a coplanar array of heat pipes. In the preferred embodiment, the cooling faces of the thermoelectric modules are placed in thermal communication with an elongated heat transfer surface defined by the cooling pipe.
In one aspect of the invention, the capillary channels in a heat pipe are generally rectangular tubes defined by the interior walls of the heat pipe. Preferably, the interior walls extend orthogonally from one face of the heat pipe to the opposing face of the heat pipe. However, the capillaries may be manufactured to have other cross-sectional configurations that are not necessarily square or rectangular in shape. The relative size of the capillaries will vary according to the 1o design requirements and characteristics of the desired cooling system. The diameter of the capillaries may be adjusted to accommodate the particular flow characteristics of a specific fluid selected for use in the system. Design characteristics, including the optimal diameters for the capillaries may be adapted to account for differences in fluid flow, heat transfer characteristics, surface is tension, and other physical properties exhibited by different refrigerants.
In a preferred embodiment, the manifold will be positioned for operation so that the capillaries will extend in a generally vertical direction. The fluid flow and heat transfer characteristics within the capillaries will be enhanced by this vertical arrangement. It is preferred that the rows of modules be positioned near the top 20 of the manifold to enhance generally downward thermal and fluid flow tendencies within the capillaries.
In a preferred embodiment, the capillaries are arranged in a single layer of capillaries within the outer walls of the heat pipes. In other instances, multiple layers of capillaries may be provided within the outer walls of a heat pipe, although in many cases, such an arrangement may not be preferred.
The manifold component is preferably made of a relatively strong, resilient, and thermally conductive material and most preferably, a metal which is not susceptible to excessive corrosion. Aluminum is a particularly useful material of construction for many applications of the present invention. Of course, persons skilled in the art will understand that other materials, including other metals, io alloys, or non metallic materials may be desirable for use in the particular conditions and circumstances under consideration.
Preferably, the fluid within the reservoir is filled until the liquid phase occupies about 40% to 70% of the volume of the reservoir. The vapor phase will occupy between about 30% and 60% of the volume of the reservoir. In a preferred is cooling application, a suitable coolant will be filled until about 60% -70% of the reservoir volume is filled with the liquid phase, and 30% - 40% of that volume is filled with the vapor phase.
Embodiments of the inventions may be made of modular components, unlike many conventional cooling system designs. For example, the cooling manifolds 2o are self contained units, and once they are disconnected from a power source, and optional control unit, may be extracted from the enclosing structure. The removed manifold or other modular components may be repaired or replaced with relative ease. Many conventional systems have complicated piping and pumping systems, expensive components and present various obstacles to repair or replacement of the refrigerating cores. Conventional pumps, compressors, and other system components are often expensive. The invention s includes embodiments which permit system designs avoiding the use of many expense conventional system components.
Other embodiments of the invention include fixed cold storage compartments provided in buildings and other structures. By way of example, modular manifold arrangements may be provided for installation along one or more interior walls of io an insulated cold storage compartment of a building. In other embodiments, refrigerator units may be manufactured for installation with storage compartments and vehicles, including truck trailers, shipping containers and other like structures.
BRIEF DESCRIPTION OF THE DRAWINGS
is In the following description, the invention is further explained in connection with a preferred embodiment making reference to the drawings in which:
Fig. 1 is a perspective, exploded representation of a refrigerator appliance in which the major components are depicted in a disassembled view.
Fig. 2 is a perspective representation of a cooling manifold wherein the major 2o comments are depicted in an exploded view.
Fig. 3 is a perspective depiction of an enlarged partial exploded view of a heat pipes and cooling pipe of the manrfold depicted in Fig. 2.
Fig. 4 is an enlarged partial view of two adjacent heat pipes depicted in Fig.
3.
Fig. 5 is an enlarged partial sectional view of several adjacent heat pipes of the s manifold and the head pipe portion the manifold shown in Fig. 2.
Fig. 6 is a perspective depiction of a partial section of an upper portion of the manifold shown in Fig. 2.
Fig. 7 is a perspective depiction of a partial section of an upper portion of the manifold shown in Fig. 2, further depicting an array of cooling fins adjacent the io upper portion of the manifold.
Fig. 8 is a perspective depiction of the air cooling components of the manifold shown in Fig. 2, depicted in exploded view.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Fig. 1 shows a refrigerator appliance as one embodiment of the present invention is in an exploded view, featuring several major components of the refrigerator.
Outer doors 100 enclose two interior compartments defined by a unitary shell 200. A cooling manifold assembly 300 includes two manifold assemblies which surround opposing side walls of shell 200. An outer housing 500 is provided to receive the other major components of the refrigerator appliance. Upper hinge mounts 510 and lower hinge mounts 520 are used to secure front doors 100 to the housing 500.
In Fig. 1, one of the two manifold assemblies is depicted in exploded view.
The manifold assembly 300 includes two opposing banks of heat pipes 320. The two banks of heat pipes are depicted in a generally, vertical arrangement. The two banks of heat pipes, when installed in the appliance, will be in thermal communication with a corresponding internal storage compartment of the appliance. The two banks of heat pipes are preferably parallel to the interior walls of the storage compartment. Each bank of heat pipes 320 is attached for to fluid communication with a corresponding head pipe 330. Refrigerant is charged within the interior chamber of the manifold. The refrigerant circulates without the use of a refrigerant pump or compressor. Each bank of heat pipes presents a substantial heat transfer area, due in part to the elongated, flat surfaces of the heat pipes. Similarly, the internal capillary structure of the heat pipes further is enhances the effective heat transfer area between the refrigerant and the interior space of the storage compartment. The substantial heat transfer area enhances the overall efficiency of the refrigeration system.
An upper cooling assembly 310 comprises a linear array of cooling fans, positioned in thermal communication above an array of thermoelectric modules 20 315 and an underlying cooling pipe 317. Fig. 3 shows an enlarged partial view of the connection established between upper ends of heat pipes 320 and corresponding fluid ports leading to the interior chamber defined by cooling pipe 317. Cooling pipe 317, in this embodiment, provides a common chamber for n circulating refrigerant contained within the manifold. The heat pipes of both opposing banks of heat pipes are in common, fluid communication with the interior chamber of the cooling pipe 317. Refrigerant contained within the manifold communicates between the interior space defined by the cooling pipe s 317 and the head pipes 330. Each head pipe 330 defines an interior space for fluid communication between the opposite (lower) ends of the respective banks of heat pipes 320. Refrigerant contained within the manifold communicates between head pipes 330 and the cooling pipe 317 via the capillary channels defined in each heat pipe. Fig. 4 shows a pair of adjacent ends of heat pipes 1o 320, arranged in a common plane, with each heat pipe having a single layer of capillary channels extending in parallel along the length of the corresponding heat pipe. The capillary channels in the heat pipes allow refrigerant to communicate between head pipes 330 and the common cooling pipe 317. With reference with Fig. 5, downwardly oriented arrows represent chilled refrigerant is traveling downwardly along the various capillary channels. Chilled refrigerant, travelling in plugs of condensed refrigerant liquid, descends along the capillary channels. At the same time, portions of the refrigerant will evaporate during operation of the manifold causing vapor plugs of the refrigerant to ascend through various capillary channels of the heat pipes (as represented by the 2o upwardly pointing arrow). Evaporated refrigerant enters into the cooling pipe 317 where the refrigerant will be chilled by the cooling operation of an array of thermoelectric modules 315.
With reference to Figs. 6, 7, and 8, a linear array of thermoelectric modules contacts a heat transfer surface defined by cooling pipe 317. The thermoelectric modules 315 are all arranged so that their respective cooling faces are in contact with cooling pipe 317. Consequently, the heating faces of the thermoelectric modules 315 face outwardly away from the cooling pipe 317. The heating faces of the thermoelectric modules 315 are in thermal communication with an upwardly projecting bank of cooling fins 314. Cooling fins 314 are arranged in parallel so that adjacent fins within the arrangement define air flow channels for air forced through the channels by a linear array of fans 312. The fans force air to across the cooling fins to remove excess heat generated by the heating faces of the thermoelectric modules 315. The fans are operated, preferably, through a control unit (not shown) set to activate the fans during operation of the thermoelectric modules 315. Similarly, the control panel (not shown) may be set to actively operate the thermoelectric modules to maintain a set, desirable is temperature for the internal storage compartment of the refrigerator appliance.
In Fig. 8, a detailed representation of the air cooling assembly is shown. As noted above, cooling pipe 317 defines a contact surface for the cooling faces of the array of thermoelectric module 315. Cooling pipe 317 includes a capped port 318 that may be used to charge and refill the manifold with a selected refrigerant.
2o The cooling assembly includes a protective gasket 316 which frames an array of thermoelectric modules 315. The gasket 316 is positioned between the lower surface of the cooling fin array 314 and the heat transfer surface defined by the cooling pipe 317. Gasket 316 protects the thermoelectric modules against accidental damage due to over tightening of the fasteners used to assemble the various components of the air cooling assembly. In addition, the gasket 316 may be provided with insulative qualities to inhibit undesirable heat transfer activity at the interface between the cooling fin array 314 and cooling pipe 317. The cooling pipe 317, the gasket 316, and the base of the cooling fin array 314 define co-axial holes for receiving bolts 311 used to secure the vertically stacked components of the cooling assembly. By way of example, bolt 311 extends through a co-axial bore defined by a fan housing in fan array 312, a bore defined by a support collar 313, the base of cooling fin array 314, a bore defined by to gasket 316, and a bore defined by cooling pipe 317. The bolts 311 are secured within the assembly by nuts (not shown).
In this embodiment, air is inducted into the air flow channels formed between opposing pairs of cooling fins 314. The flowing air is warmed upon contact with the cooling fins 314 and is exhausted near the upper end of the outer housing of is the refrigerator appliance. The heating faces of thermoelectric modules are thereby cooled to prevent overheating during operation of the refrigerator appliance.
In this illustrated embodiment, the interior compartment of the appliance includes a freezer compartment and cooling compartment. The freezer and cooling 2o compartments are arranged side by side. Two banks of heat pipes 320 i.e.
one bank from the two depicted manifolds, extend vertically through the gap formed between the freezer and chilling compartments. The first manifold, used to chill the cooling compartment, may be operated by a control panel which is separate and distinct from a second control panel used to operate the freezer compartment. The two control panels may be operated and wired independently of each other.
In the preferred embodiment, the cooling fans are arranged in two linear arrays, s in which one array of fans is positioned above the cooling manifold for the freezer compartment and a second fan array is positioned above the manifold used to cool the cooling compartment. The two cooling fan arrays are controlled independently in the preferred embodiment.
Although a refrigerator appliance is depicted in the preferred embodiment, other io embodiments will be apparent. For example, a portable cooling chest may be provided in which a manifold is used for cooling one or more interior walls of the chest. The overall size, configuration and power demands of the manifold are in part, depend upon the surface area, volume, and insulative qualities of the portable cooling chest. (A cooling chest may be designed for optimal operation is so that the chest is positioned, in its normal orientation, so that the heat pipes in the manifold define capillary channels orientated in a generally vertical direction.
In a portable cooling chest, a portable power source, including, a storage battery or portable generator may be provided to power a pre-selected number of thermoelectric modules to cool the internal compartment of the chest. One or 2o more cooling fans may be provided, as required. A cooling chest may also be provided with adapters to convert AC power to a DC power supply for the thermoelectric modules. Similarly, adapters may be provided to connect with is power outlets in vehicles for powering accessories. Other power source arrangements may also be provided.
The thermoelectric modules are supplied with electric current from a suitable power source which is not shown. The power source is typically a DC power unit s selected with the appropriate operational requirements for the thermoelectric modules and heat transfer requirements for the particular application.
A wide range of refrigerants may be used in the manifold of the invention, including conventional refrigerants. However, the following are two examples of preferred refrigerants, identified as OS-12bT"" and OS-12aT"", which are believed 1o to offer certain environmental advantages, as compared to selected conventional refrigerants.
Table 1 1) OS-l2bTM
Classification OS-12b HCFC-22 HFC-1 Molecular mass 113.38 120.93 102.03 Boiling temperature( -26.59 -29.8 -26.5 C) Heat of vaporization 248.3 149.8 198.7 at 0 C(KJ/Kg) Stabilities Thermal Stable Stable Stable Chemical Stable Stable Stable Erosive No No No Flammability(LFL None None None & UFL) Autoignition temperature( C) None None None Toxicity No No No O.D.P.(Ozone depletion potential) 0 1 0 G.W.P.(Global warming potential <3 8,100 1,300 in relation to C02 with 100 years integration time) Lubricant Mineral Mineral Ester 2) OS-l2aTM
Classification OS-12a HCFC-22 HFC-1 Molecular mass 57.9 120.93 102.03 Boiling temperature( -34.5 -29.8 -26.5 C) Heat of vaporization 367.0 149.8 198.7 at 0 C(KJ/Kg) Stabilities Thermal Stable Stable Stable Chemical Stable Stable Stable Erosive No No No Flammability(LFL 3.7-9.5% None None & UFL) Autoignition temperature( 540 None None C) Toxicity No No No O.D.P.(Ozone depletion 0 1 0 potential) G.W.P.(Global warming 3 8,100 1,300 potential in relation to C02 with 100 years integration time) Lubricant Mineral/EsterMineral Ester 4 , The above Table 1 is reproduced from information published by Technochem CO., Ltd. (htt~//www.technochem.com), Republic of Korea.
TM _ Trade-mark of Technochem Co., Ltd., Republic of Korea Of course, other refrigerants may be selected for various reasons. After a s suitable refrigerant is selected, it is preferable to evacuate entrapped air from the interior of the manifold, during manufacture of the manifold. For example, the air may be evacuated through an access port. In the preferred embodiment, substantially all of the entrapped air will be removed and thereafter, the refrigerant will be charged into the interior of the reservoir of the manifold.
io Certain other refrigerants will also be preferred for certain applications.
For example, conventional refrigerants such as R-142, R-141 B and others may be used in cooling applications with a suitably adapted heat exchange manifold.
With respect to the heat pipe design, it is believed that capillaries with cross-sectional diameters of about 4 mm in diameter were particularly efficient in is refrigeration applications. In some instances, it may be desirable to use capillaries with smaller effective diameters. Capillary tubes that are generally rectangular when viewed in cross section may have dimensions of 1 mm X 1.4 mm or lower. In other instances, the capillaries may have cross-sectional dimensions of about 0.5 mm X 0.6 mm. Of course, other sizes of capillaries may Zo be selected, based on various design considerations.
i8 However, the optimal size of the capillaries may vary according to the physical properties of the thermally conductive fluid selected for use in a particular heat exchange system. For example, surface tension, fluid viscosity and other factors may affect the optimal effective diameter of the capillaries in a particular system.
A number of factors may affect fluid performance and thus affect the optimal and maximum diameters of the capillaries to be provided in the refrigeration system.
It will be appreciated that refrigerants will tend to flow within the internal channels of the manifold due in part to cooling of the fluid and the capillary action exerted on the fluid within the capillaries of the manifold. One of the advantages of the io invention is that it is unnecessary to provide a circulating pump to circulate the refrigerant within the interior chamber of the manifold. Although there may be instances where a circulating pump may be added, such a pump would not be necessary to circulate the refrigerant provided within the manifold.
The present invention has been described with reference to preferred is embodiments. However, other embodiments of the invention, and variations and modifications thereof will be apparent to those persons having ordinary skill in the art. It is intended that those other embodiments, variations and modifications thereof, will be included within the scope of the present invention as claimed within the appended claims.
Claims (32)
1. A refrigeration apparatus comprising:
A structure defining an interior storage compartment;
a manifold for cooling the interior storage compartment;
the manifold defining an inner chamber for an effective amount of a refrigerant, the inner chamber comprising:
an elongated first chamber, an elongated second chamber, and a plurality of capillary channels defined by heat pipes extending between the first and second chambers;
a pre-selected number of thermoelectric modules arranged in cooling, thermal communication with the manifold; and an air blower for thermal communication with heating faces defined by the thermoelectric modules.
A structure defining an interior storage compartment;
a manifold for cooling the interior storage compartment;
the manifold defining an inner chamber for an effective amount of a refrigerant, the inner chamber comprising:
an elongated first chamber, an elongated second chamber, and a plurality of capillary channels defined by heat pipes extending between the first and second chambers;
a pre-selected number of thermoelectric modules arranged in cooling, thermal communication with the manifold; and an air blower for thermal communication with heating faces defined by the thermoelectric modules.
2. The apparatus claimed in claim 1 comprising a plurality of heat pipes, each heat pipe defining an elongated first planar surface adjacent an interior wall of the storage compartment.
3. The apparatus claimed in claim 2, wherein the plurality of heat pipes define two elongated, parallel planar surfaces.
4. The apparatus claimed in claim 1, wherein the amount of the refrigerant fluid comprises between about 40% and 70% liquid by volume and between about 30% and 60% vapor by volume.
5. The apparatus claimed in claim 1, wherein the heat pipes define a planar array parallel to an interior wall of the structure.
6. The apparatus claimed in claim 5, wherein the heat pipes define two parallel, offset, planar surfaces adjacent two interior walls of said structure.
7. The apparatus claimed in claim 6, wherein the structure comprises two adjacent enclosed spaces, one of which enclosed spaces is a freezer compartment.
8. The apparatus claimed in claim 1, comprising a portable power source for the thermoelectric modules.
9. The apparatus claimed in claim 8, comprising a console for controlling the temperature of the interior storage compartment.
10. The apparatus claimed in claim 1, wherein the heat pipes define two opposing walls parallel to two opposite side walls of the structure.
11. The apparatus claimed in claim 1, wherein the first chamber receives first ends of said heat pipes, said heat pipes defining two opposing planar banks of heat pipes.
12. The apparatus claimed in claim 11, wherein the first chamber defines an elongated planar surface in thermal communication with the thermoelectric modules.
13. The apparatus claimed in claim 12, wherein a plurality of cooling fins are positioned in thermal communication with heating faces defined by the thermoelectric modules.
14. The apparatus claimed in claim 12, wherein the thermoelectric modules are in a linear array and define heating faces in thermal communication with an air stream.
15. The apparatus claimed in claim 14, wherein the air stream is pumped by one or more fans.
16. The apparatus claimed in claim 15, wherein the fans are arranged in a linear array, the cooling fins are positioned between the linear array of fans and the heating faces of the thermoelectric modules.
17. The apparatus claimed in claim 16, wherein the plurality of cooling fins defines an array of gaps, defining channels for fluid communication of the air stream between said heating faces of said thermoelectric modules and said plurality of fans.
18. A refrigeration device comprising:
a housing defining one or more closable interior spaces in thermal communication with one or more manifolds, each manifold defining an inner chamber for an effective amount of a refrigerant, the inner chamber comprising:
a first cylinder, a second cylinder, and a plurality of capillary channels defined by heat pipes in fluid communication between said first and second cylinders; and a preselected number of thermoelectric modules arranged in cooling, thermal communication with the manifold; and one or more blowers for thermal communication between an air stream and heating faces defined by said preselected number of thermoelectric modules.
a housing defining one or more closable interior spaces in thermal communication with one or more manifolds, each manifold defining an inner chamber for an effective amount of a refrigerant, the inner chamber comprising:
a first cylinder, a second cylinder, and a plurality of capillary channels defined by heat pipes in fluid communication between said first and second cylinders; and a preselected number of thermoelectric modules arranged in cooling, thermal communication with the manifold; and one or more blowers for thermal communication between an air stream and heating faces defined by said preselected number of thermoelectric modules.
19. The device claimed in claim 18, wherein the first cylinder defines a first heat transfer surface in thermal communication with cooling faces defined by the thermoelectric modules.
20. The device claimed in claim 19, wherein the plurality of heat pipes define one or more planar banks of heat pipes, the planar banks being parallel to one or more interior walls defined by the housing.
21. The device claimed in claim 18, wherein the manifolds define at least two opposing banks of heat pipes parallel to a corresponding number of interior walls of the housing.
22. The device claimed in claim 21, wherein the banks of heat pipes are in fluid communication with a common first cylinder.
23. The device claimed in claim 22, wherein the first cylinder defines an elongated thermal transfer surface in thermal communication with a linear array of said thermoelectric modules.
24. The device claimed in claim 23, comprising a plurality of cooling fins positioned in thermal communication with said heating faces.
25. The device claimed in claim 24, wherein the cooling fins define a plurality of gaps, the gaps defining channels for thermal communication between said heating faces and the air stream.
26. The device claimed in claim 25, wherein the blowers comprise fans in a linear array adjacent said heating faces.
27. The device claimed in claim 26, wherein a second manifold communicates with a second closable space defined by the housing, the second closable space being adjacent to the first closable space, both spaces being in thermal communication with the thermoelectric modules.
28. A refrigeration device claimed in claim 18, comprising a first blower operatively connected to force air through a plurality of heat transfer channels defined by a plurality of cooling fins in thermal communication with a heat transfer surface defined by an array of aligned heating faces of said thermoelectric modules.
29. The apparatus claimed in claim 28, comprising a control panel for selectively operating the thermoelectric modules according to a pre-selected temperature setting for the closable interior space defined by the housing.
30. The refrigeration device claimed in claim 29, comprising a portable power source for said thermoelectric modules.
31. The refrigeration device claimed in claim 18, wherein the device is designed for portable transport, the device comprising one or more handles for portable transport.
32. The refrigeration device claimed in claim 31, wherein said handle is supported by the housing.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR2001-21998 | 2001-07-20 | ||
| KR2020010022000U KR200252832Y1 (en) | 2001-07-20 | 2001-07-20 | Air conditioner for use of heat pipe |
| KR2020010021998U KR200259618Y1 (en) | 2001-07-20 | 2001-07-20 | Heating exchanger for use of solar collector |
| KR2001-22000 | 2001-07-20 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2394474A1 true CA2394474A1 (en) | 2003-01-20 |
Family
ID=26639016
Family Applications (4)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002467692A Abandoned CA2467692A1 (en) | 2001-07-20 | 2002-07-18 | Heat exchanger assembly and heat exchange manifold |
| CA002394463A Abandoned CA2394463A1 (en) | 2001-07-20 | 2002-07-22 | Air conditioner with heat pipe |
| CA002394468A Abandoned CA2394468A1 (en) | 2001-07-20 | 2002-07-22 | Solar energy heater with heat pipe and heat exchanger |
| CA002394474A Abandoned CA2394474A1 (en) | 2001-07-20 | 2002-07-22 | Refrigeration units and heat pipe |
Family Applications Before (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002467692A Abandoned CA2467692A1 (en) | 2001-07-20 | 2002-07-18 | Heat exchanger assembly and heat exchange manifold |
| CA002394463A Abandoned CA2394463A1 (en) | 2001-07-20 | 2002-07-22 | Air conditioner with heat pipe |
| CA002394468A Abandoned CA2394468A1 (en) | 2001-07-20 | 2002-07-22 | Solar energy heater with heat pipe and heat exchanger |
Country Status (7)
| Country | Link |
|---|---|
| US (3) | US6807811B2 (en) |
| JP (1) | JP2004537705A (en) |
| KR (1) | KR20040052214A (en) |
| CN (1) | CN1556912A (en) |
| AU (1) | AU2002334267A1 (en) |
| CA (4) | CA2467692A1 (en) |
| WO (1) | WO2003012357A2 (en) |
Families Citing this family (103)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7946120B2 (en) | 2001-02-09 | 2011-05-24 | Bsst, Llc | High capacity thermoelectric temperature control system |
| US7942010B2 (en) | 2001-02-09 | 2011-05-17 | Bsst, Llc | Thermoelectric power generating systems utilizing segmented thermoelectric elements |
| US6672076B2 (en) | 2001-02-09 | 2004-01-06 | Bsst Llc | Efficiency thermoelectrics utilizing convective heat flow |
| US7273981B2 (en) * | 2001-02-09 | 2007-09-25 | Bsst, Llc. | Thermoelectric power generation systems |
| CN100419347C (en) * | 2001-08-07 | 2008-09-17 | Bsst公司 | Thermoelectric personal environment appliance |
| US20050103327A1 (en) * | 2003-11-18 | 2005-05-19 | Atomic Energy Council - Institute Of Nuclear Energy Research | Passive energy saving system for a building |
| US7380586B2 (en) | 2004-05-10 | 2008-06-03 | Bsst Llc | Climate control system for hybrid vehicles using thermoelectric devices |
| US20060075758A1 (en) | 2004-10-07 | 2006-04-13 | Tigerone Development, Llc; | Air-conditioning and heating system utilizing thermo-electric solid state devices |
| US7587818B2 (en) * | 2004-12-23 | 2009-09-15 | General Electric Company | Repair of gas turbine blade tip without recoating the repaired blade tip |
| CN100343785C (en) * | 2005-01-10 | 2007-10-17 | 富准精密工业(深圳)有限公司 | Pulsating type heat transmission device |
| US20080099191A1 (en) * | 2005-02-02 | 2008-05-01 | Carrier Corporation | Parallel Flow Heat Exchangers Incorporating Porous Inserts |
| KR100642006B1 (en) * | 2005-02-18 | 2006-11-13 | 주식회사 웰바스 | A water-cooled barbecue system |
| US7743614B2 (en) | 2005-04-08 | 2010-06-29 | Bsst Llc | Thermoelectric-based heating and cooling system |
| US7913685B2 (en) * | 2005-05-18 | 2011-03-29 | Barbara Hildegard Pause | Textile heat accumulator for utilization of solar energy |
| EP2282357B1 (en) * | 2005-06-28 | 2015-12-02 | Gentherm Incorporated | Thermoelectric power generator for variable thermal power source |
| US8783397B2 (en) | 2005-07-19 | 2014-07-22 | Bsst Llc | Energy management system for a hybrid-electric vehicle |
| US7310953B2 (en) * | 2005-11-09 | 2007-12-25 | Emerson Climate Technologies, Inc. | Refrigeration system including thermoelectric module |
| US20070101737A1 (en) | 2005-11-09 | 2007-05-10 | Masao Akei | Refrigeration system including thermoelectric heat recovery and actuation |
| US7779639B2 (en) | 2006-08-02 | 2010-08-24 | Bsst Llc | HVAC system for hybrid vehicles using thermoelectric devices |
| US20100155018A1 (en) | 2008-12-19 | 2010-06-24 | Lakhi Nandlal Goenka | Hvac system for a hybrid vehicle |
| DE102006052122B4 (en) * | 2006-11-06 | 2009-07-30 | Rittal Gmbh & Co. Kg | Air conditioning device |
| KR100811976B1 (en) * | 2006-11-08 | 2008-03-10 | 이근진 | A water-cooled barbecue system |
| CN116558147A (en) | 2007-05-25 | 2023-08-08 | 詹思姆公司 | System and method for thermoelectric heating and cooling |
| JP2009040803A (en) * | 2007-08-06 | 2009-02-26 | National Institute Of Advanced Industrial & Technology | Heat transmitting medium |
| KR100861005B1 (en) * | 2007-08-10 | 2008-09-30 | 연세대학교 산학협력단 | Air-conditioner comprised thermoelectric module and heat pipe |
| US20090084112A1 (en) * | 2007-10-02 | 2009-04-02 | Demetrius Calvin Ham | Thermoelectric vehicle engine air cooler |
| CN103398494B (en) * | 2008-03-05 | 2017-03-01 | 史泰克公司 | Cooling system and the method for operation thermoelectric cooling system |
| CN101978517A (en) * | 2008-03-19 | 2011-02-16 | 史泰克公司 | Metal-core thermoelectric cooling and power generation device |
| US8701422B2 (en) | 2008-06-03 | 2014-04-22 | Bsst Llc | Thermoelectric heat pump |
| JP2011529169A (en) | 2008-07-22 | 2011-12-01 | ザ リージェンツ オブ ザ ユニバーシティ オブ カリフォルニア | Mini channel solar collector |
| US20100024859A1 (en) * | 2008-07-29 | 2010-02-04 | Bsst, Llc. | Thermoelectric power generator for variable thermal power source |
| WO2010040137A1 (en) * | 2008-10-03 | 2010-04-08 | Andrew Lowenstein | Solar energy collection |
| US9555686B2 (en) | 2008-10-23 | 2017-01-31 | Gentherm Incorporated | Temperature control systems with thermoelectric devices |
| US9447994B2 (en) | 2008-10-23 | 2016-09-20 | Gentherm Incorporated | Temperature control systems with thermoelectric devices |
| EP2349753B1 (en) | 2008-10-23 | 2016-11-23 | Gentherm Incorporated | Multi-mode hvac system with thermoelectric device |
| US8074456B2 (en) * | 2008-10-29 | 2011-12-13 | Hewlett-Packard Development Company, L.P. | Thermal management system having thermoelectric modules |
| US20120006383A1 (en) * | 2008-11-20 | 2012-01-12 | Donnelly Sean M | Heat exchanger apparatus and methods of manufacturing cross reference |
| US8925543B2 (en) * | 2009-01-13 | 2015-01-06 | Aerojet Rocketdyne Of De, Inc. | Catalyzed hot gas heating system for pipes |
| US7987844B2 (en) * | 2009-01-13 | 2011-08-02 | Hamilton Sundstrand Corporation | Catalyzed hot gas heating system for concentrated solar power generation systems |
| US8359871B2 (en) * | 2009-02-11 | 2013-01-29 | Marlow Industries, Inc. | Temperature control device |
| US8347877B2 (en) * | 2009-02-19 | 2013-01-08 | Mill Masters, Inc. | Solar energy collecting system and method |
| KR20170036119A (en) | 2009-05-18 | 2017-03-31 | 젠썸 인코포레이티드 | Battery thermal management system |
| CN104914896B (en) | 2009-05-18 | 2017-06-13 | 詹思姆公司 | temperature control system with thermoelectric device |
| US8904808B2 (en) | 2009-07-17 | 2014-12-09 | Sheetak, Inc. | Heat pipes and thermoelectric cooling devices |
| MY165359A (en) | 2009-11-23 | 2018-03-21 | Siang Teik Teoh | Coaxial tube solar heater with nighttime cooling |
| WO2011067773A1 (en) * | 2009-12-06 | 2011-06-09 | Heliofocus Ltd. | Thermal generation systems |
| CN101764167B (en) * | 2009-12-25 | 2011-08-24 | 赵耀华 | High-efficient solar photovoltaic cell heat dissipating device and electricity and heat cogeneration system |
| US20110226233A1 (en) * | 2010-03-19 | 2011-09-22 | John Randall Schwarz | Method and Apparatus for Collecting Solar Energy |
| GB2479867B (en) * | 2010-04-26 | 2016-03-02 | ECONOTHERM UK Ltd | Heat exchanger |
| KR100984280B1 (en) | 2010-04-23 | 2010-09-30 | 김봉석 | Heat exchanging apparatus of refrigerant composition of freezing cycle |
| CN101886836B (en) * | 2010-06-29 | 2012-09-05 | 清华大学 | Machine room heat removal device for evaporation cooling type heat-pipe heat exchange |
| US20130291564A1 (en) * | 2011-01-13 | 2013-11-07 | Sheetak, Inc. | Thermoelectric cooling systems |
| KR101196375B1 (en) * | 2011-03-03 | 2012-11-02 | 주식회사동양강철 | Cooler having heat pipe combined heat sink |
| US20120266608A1 (en) * | 2011-04-25 | 2012-10-25 | Delphi Technologies, Inc. | Thermoelectric heat exchanger capable of providing two different discharge temperatures |
| EP2518424B1 (en) * | 2011-04-25 | 2018-11-28 | MAHLE International GmbH | Thermoelectric heat exchanger capable of providing two different discharge temperatures |
| US9725966B2 (en) | 2011-06-10 | 2017-08-08 | Magma Global Limited | Riser system |
| US9157659B2 (en) | 2011-06-15 | 2015-10-13 | Ail Research Inc. | Solar energy collection |
| KR101950468B1 (en) | 2011-07-11 | 2019-02-20 | 젠썸 인코포레이티드 | Thermoelectric-based thermal management of electrical devices |
| US9909789B2 (en) | 2012-01-10 | 2018-03-06 | Spring (U.S.A.) Corporation | Heating and cooling unit with canopy light |
| US8850829B2 (en) | 2012-01-10 | 2014-10-07 | Spring (U.S.A.) Corporation | Heating and cooling unit with semiconductor device and heat pipe |
| US20130291555A1 (en) | 2012-05-07 | 2013-11-07 | Phononic Devices, Inc. | Thermoelectric refrigeration system control scheme for high efficiency performance |
| WO2013169774A2 (en) | 2012-05-07 | 2013-11-14 | Phononic Devices, Inc. | Thermoelectric heat exchanger component including protective heat spreading lid and optimal thermal interface resistance |
| DE102012211259A1 (en) * | 2012-06-29 | 2014-01-02 | Behr Gmbh & Co. Kg | Thermoelectric temperature control unit |
| CN102851708A (en) * | 2012-08-07 | 2013-01-02 | 江苏晨力环保科技有限公司 | Cooling device for electrolytic bath |
| CN104822994B (en) * | 2012-11-26 | 2017-09-26 | 旭化成住宅株式会社 | Radiate panel assembly |
| US9182157B2 (en) | 2012-12-03 | 2015-11-10 | Whirlpool Corporation | On-door ice maker cooling |
| US9593870B2 (en) | 2012-12-03 | 2017-03-14 | Whirlpool Corporation | Refrigerator with thermoelectric device for ice making |
| US9151524B2 (en) | 2012-12-03 | 2015-10-06 | Whirlpool Corporation | Refrigerator with icemaker chilled by thermoelectric device cooled by fresh food compartment air |
| US9115918B2 (en) | 2012-12-03 | 2015-08-25 | Whirlpool Corporation | Refrigerator with icemaker chilled by thermoelectric device cooled by fresh food compartment air |
| DK3047219T3 (en) | 2013-09-16 | 2017-08-14 | Phononic Devices Inc | IMPROVED HEAT TRANSPORT SYSTEMS FOR COOLING ROOMS AND SURFACES |
| CN103542478B (en) * | 2013-11-18 | 2016-06-01 | 北京德能恒信科技有限公司 | A kind of semiconductor air conditioner |
| KR20150075122A (en) * | 2013-12-18 | 2015-07-03 | 현대자동차주식회사 | Heat exchanger with thermoelectric element |
| CN103759563B (en) * | 2014-02-21 | 2015-12-09 | 电子科技大学 | A kind of microchannel heat sink utilizing phase-change circulation of working medium motion heat transfer |
| US9593871B2 (en) | 2014-07-21 | 2017-03-14 | Phononic Devices, Inc. | Systems and methods for operating a thermoelectric module to increase efficiency |
| US10458683B2 (en) | 2014-07-21 | 2019-10-29 | Phononic, Inc. | Systems and methods for mitigating heat rejection limitations of a thermoelectric module |
| KR20160063003A (en) * | 2014-11-26 | 2016-06-03 | 삼성전자주식회사 | Thermoelectric device |
| CN104534781B (en) * | 2014-12-15 | 2016-11-23 | 青岛海尔股份有限公司 | Cold end heat-exchanger rig and semiconductor freezer |
| CN104613804B (en) * | 2014-12-15 | 2017-03-01 | 青岛海尔股份有限公司 | Bending pipe fitting and the semiconductor freezer with this bending pipe fitting |
| CN104567175B (en) * | 2014-12-15 | 2016-11-23 | 青岛海尔股份有限公司 | Semiconductor freezer |
| US10603976B2 (en) | 2014-12-19 | 2020-03-31 | Gentherm Incorporated | Thermal conditioning systems and methods for vehicle regions |
| US10391831B2 (en) * | 2015-07-23 | 2019-08-27 | Hyundai Motor Company | Combined heat exchanger module |
| WO2017035043A1 (en) * | 2015-08-24 | 2017-03-02 | Abengoa Solar Llc. | Solar receiver using heat pipes and granular thermal storage medium |
| US10625566B2 (en) | 2015-10-14 | 2020-04-21 | Gentherm Incorporated | Systems and methods for controlling thermal conditioning of vehicle regions |
| RU2630069C1 (en) * | 2016-04-11 | 2017-09-05 | Федеральное государственное бюджетное образовательное учреждение высшего образования "Юго-Западный государственный университет" (ЮЗГУ) | Complex electric generating heating device |
| CN205808194U (en) * | 2016-06-13 | 2016-12-14 | 深圳市英维克科技股份有限公司 | Heat exchanger module |
| USD811802S1 (en) | 2016-07-15 | 2018-03-06 | Spring (U.S.A.) Corporation | Food server |
| US11839062B2 (en) * | 2016-08-02 | 2023-12-05 | Munters Corporation | Active/passive cooling system |
| US11255611B2 (en) * | 2016-08-02 | 2022-02-22 | Munters Corporation | Active/passive cooling system |
| CN108731508B (en) * | 2017-04-18 | 2021-07-20 | 浙江盾安机械有限公司 | Capillary heat exchanger |
| CN109506353A (en) * | 2017-09-14 | 2019-03-22 | 昆山开思拓空调技术有限公司 | A kind of capillary air conditioning terminal using free convection |
| PL126975U1 (en) * | 2018-01-24 | 2019-07-29 | Marcin Melanż | Heater in an instrument fitting |
| US10688845B2 (en) * | 2018-08-13 | 2020-06-23 | Caterpillar Paving Products Inc. | Cooling package for a machine |
| US10876765B2 (en) | 2018-11-28 | 2020-12-29 | Element 16 Technologies, Inc. | Systems and methods of thermal energy storage |
| US11892238B2 (en) | 2019-06-03 | 2024-02-06 | Sonoco Development, Inc. | Heat pipe cooled pallet shipper |
| RU2710210C1 (en) * | 2019-06-13 | 2019-12-25 | Федеральное государственное бюджетное образовательное учреждение высшего образования "Юго-Западный государственный университет" (ЮЗГУ) | Electric generating heater |
| TW202120037A (en) * | 2019-07-22 | 2021-06-01 | 美商布魯克斯熱傳導公司 | Thermal management device and system |
| CN110686414B (en) * | 2019-10-26 | 2020-12-04 | 北京工业大学 | Compound parabolic light-gathering power generation-phase change heat storage device |
| US11313625B2 (en) * | 2019-12-16 | 2022-04-26 | Yuan-Hsin Sun | Intensified cassette-type heat dissipation module |
| CN114096108B (en) * | 2020-08-24 | 2023-03-24 | 华为技术有限公司 | Heat sink and method for manufacturing the same |
| CN112594769B (en) * | 2020-12-24 | 2022-01-04 | 三峡大学 | Multi-energy supply device and method based on aluminum micro-channel heat pipe technology |
| CA3233607A1 (en) * | 2021-10-01 | 2023-04-06 | Bootbox Labs, Inc. | Temperature control unit |
| GB2621968A (en) * | 2022-02-17 | 2024-03-06 | Botanic Energy Ltd | Improvements to heat pumps |
| CN114413326B (en) * | 2022-03-29 | 2022-06-07 | 煤炭工业太原设计研究院集团有限公司 | Solar heat pipe air conditioning system and control method thereof |
Family Cites Families (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4019098A (en) * | 1974-11-25 | 1977-04-19 | Sundstrand Corporation | Heat pipe cooling system for electronic devices |
| US4470450A (en) * | 1981-10-22 | 1984-09-11 | Lockheed Missiles & Space Co. | Pump-assisted heat pipe |
| DE3320632A1 (en) | 1983-06-08 | 1984-12-13 | Hoechst Ag, 6230 Frankfurt | HEAT EXCHANGER |
| US5653111A (en) | 1993-07-07 | 1997-08-05 | Hydrocool Pty. Ltd. | Thermoelectric refrigeration with liquid heat exchange |
| JP3369349B2 (en) * | 1995-03-02 | 2003-01-20 | 株式会社エコ・トゥエンティーワン | Thermoelectric converter |
| US6058712A (en) * | 1996-07-12 | 2000-05-09 | Thermotek, Inc. | Hybrid air conditioning system and a method therefor |
| US5752566A (en) * | 1997-01-16 | 1998-05-19 | Ford Motor Company | High capacity condenser |
| US5860472A (en) * | 1997-09-03 | 1999-01-19 | Batchelder; John Samual | Fluid transmissive apparatus for heat transfer |
| AU749183B2 (en) * | 1997-10-06 | 2002-06-20 | Matsushita Refrigeration Company | Manifold incorporating a thermoelectric module and a cooling device using the thermoelectric module |
| US6155075A (en) * | 1999-03-18 | 2000-12-05 | Lennox Manufacturing Inc. | Evaporator with enhanced refrigerant distribution |
| JP3578693B2 (en) | 1999-10-14 | 2004-10-20 | 株式会社コーアガス日本 | Air / hot water type gas production plant |
| JP4686062B2 (en) | 2000-06-26 | 2011-05-18 | 昭和電工株式会社 | Evaporator |
| US6536517B2 (en) * | 2000-06-26 | 2003-03-25 | Showa Denko K.K. | Evaporator |
| US6598405B2 (en) * | 2001-02-09 | 2003-07-29 | Bsst Llc | Thermoelectric power generation utilizing convective heat flow |
-
2002
- 2002-07-18 KR KR1020047001053A patent/KR20040052214A/en not_active Application Discontinuation
- 2002-07-18 JP JP2003517510A patent/JP2004537705A/en active Pending
- 2002-07-18 AU AU2002334267A patent/AU2002334267A1/en not_active Abandoned
- 2002-07-18 WO PCT/IB2002/003701 patent/WO2003012357A2/en active Application Filing
- 2002-07-18 CA CA002467692A patent/CA2467692A1/en not_active Abandoned
- 2002-07-18 CN CNA028147022A patent/CN1556912A/en active Pending
- 2002-07-22 CA CA002394463A patent/CA2394463A1/en not_active Abandoned
- 2002-07-22 US US10/200,601 patent/US6807811B2/en not_active Expired - Fee Related
- 2002-07-22 CA CA002394468A patent/CA2394468A1/en not_active Abandoned
- 2002-07-22 US US10/200,554 patent/US20030029174A1/en not_active Abandoned
- 2002-07-22 CA CA002394474A patent/CA2394474A1/en not_active Abandoned
- 2002-07-22 US US10/200,555 patent/US20030037907A1/en not_active Abandoned
Also Published As
| Publication number | Publication date |
|---|---|
| US20030029174A1 (en) | 2003-02-13 |
| WO2003012357A2 (en) | 2003-02-13 |
| CA2394463A1 (en) | 2003-01-20 |
| US20030029175A1 (en) | 2003-02-13 |
| US20030037907A1 (en) | 2003-02-27 |
| CA2467692A1 (en) | 2003-02-13 |
| WO2003012357A3 (en) | 2004-05-06 |
| AU2002334267A1 (en) | 2003-02-17 |
| CA2394468A1 (en) | 2003-01-20 |
| JP2004537705A (en) | 2004-12-16 |
| US6807811B2 (en) | 2004-10-26 |
| KR20040052214A (en) | 2004-06-22 |
| CN1556912A (en) | 2004-12-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20030029174A1 (en) | Refrigeration units and heat pipe | |
| US6003319A (en) | Thermoelectric refrigerator with evaporating/condensing heat exchanger | |
| US7246505B2 (en) | Personal air conditioning system | |
| CN101809388B (en) | Refrigerator | |
| US20020134544A1 (en) | Passive cooling system and method | |
| EP1167886A2 (en) | Cooling and heating system and air circulation panel | |
| EP1130344B1 (en) | Domestic refrigerator with peltier effect, heat accumulators and evaporative thermosyphons | |
| US20070101730A1 (en) | Cold stocker | |
| CN111765704A (en) | Air-cooled refrigerating system and semiconductor refrigerator | |
| KR100907338B1 (en) | Refrigerator car using cold storage material | |
| KR101429164B1 (en) | Brine heat exchange type Cold Storage Module. | |
| KR101429163B1 (en) | Easier to assemble the puzzle-type Cold Storage Module. | |
| WO2002016836A1 (en) | Stirling cooling device, cooling chamber, and refrigerator | |
| JP5964702B2 (en) | Refrigerator | |
| KR102034439B1 (en) | Soju freezer for camping | |
| KR102034440B1 (en) | Soju freezer for camping | |
| KR200311024Y1 (en) | refrigerater for rice | |
| JP2009192102A (en) | Cooling storage device and cool box | |
| JP2014167380A (en) | Cold insulation box with cold storage function and cold storage method using the same | |
| EP3943845A1 (en) | Refrigerator | |
| CN220205943U (en) | Bathroom air conditioner | |
| EP3943846A1 (en) | Refrigerator | |
| CN117516061A (en) | Heat exchange device and storage equipment | |
| JP2006090684A (en) | Refrigerator | |
| JP2008170032A (en) | Condenser, cooling system and refrigerator |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |