US3759321A - Condenser coil apparatus - Google Patents
Condenser coil apparatus Download PDFInfo
- Publication number
- US3759321A US3759321A US00191873A US3759321DA US3759321A US 3759321 A US3759321 A US 3759321A US 00191873 A US00191873 A US 00191873A US 3759321D A US3759321D A US 3759321DA US 3759321 A US3759321 A US 3759321A
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- US
- United States
- Prior art keywords
- coil
- refrigerant
- fan
- air
- circumscribed
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/14—Heat exchangers specially adapted for separate outdoor units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/46—Component arrangements in separate outdoor units
- F24F1/48—Component arrangements in separate outdoor units characterised by air airflow, e.g. inlet or outlet airflow
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
Definitions
- the present invention seeks to improve the construction of the split system condenser-compressor package, particularly by reducing the size and cost of the package, by eliminating certain of the casing components, and by more effectively utilizing the space occupied by the package.
- FIGS. 1, 2 and 3 are schematic representations illustrating the operation of three different condenser fancoil arrangements
- FIG. 4 is a sectional view taken through a condensercompressor assembly constructed according to this invention.
- FIG. 5 is a sectional view taken on lines 55 in FIG. 4;
- FIG. 6 is a fragmentary sectional view of a detail used in the FIG. 5 construction
- FIG. 7 is a view of a detail that can be used in of the FIG. 6 detail
- FIG. 8 is a fragmentary view of a corner construction useful as an alternate in the FIG. 5 assembly
- FIG. 9 shows a detail that can be used to mount a venturi panel in the FIG. 4 construction
- FIG. 10 is a schematic representation of a refrigerant coil passage arrangement useful in practice of the invention..
- FIG. 1 schematically illustrates a fan-coil arrange ment comprising an air duct 10 having a venturi panel 12 in which is located a propeller fan wheel 14 for moving air rightwardly through a plate fin refrigerant coil 16.
- the coil has two rows of refrigerant tubes 18 extending transversely through plate fins 20, said fins having leading edges 22 and trailing edges 24.
- FIG. 2 shows a fan-coil unit very similar to the FIG. 1 unit except that the coil is comprised of two coil sections 16a and 16b.
- the two coils have twice the number of leading edges and twice the number of trailing edges as compared with FIG. 1; assuming the same volumetric air flow, the FIG. 2 coil arrangement therefore provides a somewhat higher heat transfer capability because the extended (fin) surface temperature does not conduct to cooler tubes within the coil core, normally downstream in a counter flow (air vs. refrigerant) arrangement.
- the amount of leading fin edge is doubled or tripled (depending on comparison to a comparable 2 or 3 row capacity coil) thus increasing the resultant heat transfer area of the extended surface.
- the air flow resistance pressure drop characteristic
- FIG. 3 shows a fan-coil arrangement having the same number of refrigerant tubes as the coils in the FIG. 1
- FIG. 3 the coil has one row of tubes, arranged eight tubes per row.
- the heat transfer capability of the FIG. 3 unit is somewhat less than that of the FIG. 2 unit because of a lesser linear air velocity through the FIG. 3 unit (assuming the same volumetric air flow for each unit).
- FIG. 1 coil has a face area of 2 square feet, and that fan 14 provides a linear velocity of 400 feet per minute
- the volumetric air flow through the FIG. 1 unit will be 800 cubic feet per minute.
- the heat transfer capability of the FIG. 2 unit will be greater because of the single row design, as previously noted.
- the air flow resistance (pressure-drop characteristic) for the FIG. 1 and FIG. 2 units will be the same.
- the FIG. 3 unit will have a volumetric flow requirement twice that of the FIG. 1 or FIG. 2 units, namely 1,600 cubic feet per minute.
- the higher volumetric flow requirement of the FIG. 3 unit makes less desirable than the FIG. 1 or FIG. 2 units because of the larger duct dimensions and higher noise emission.
- the FIG. 2 unit combines the best characteristics of the three arrangements, i.e., a low volumetric air flow requirement and a high inherent heat transfer capability as previously noted in the FIG. 2 description.
- FIGS. 4 and 5 plate, fins 20a and 2017 from a vertical inlet header 42(FIG. 5) around the annular circumference of the unit to other headers designated 44 in FIG. 5.
- the tubes 18a and 18b are arranged horizontally one above another, and that the plate fins are arranged vertically in planes generally normal to the sides of the square outline (except at the comers).
- each coil 16a and 16b is provided with six heat exchange tubes arranged in a single row. In practice a greater number of tubes would be provided, depending on the size of the condenser, i.e., condensing requirement.
- the space circumscribed by coil sections 16a and 16b is occupied by a fan which comprises a fan motor 42 and a propeller fan wheel 44.
- the fan motor is suspended from a diffuser cone 46 which connects with the top panel 32: the motor could be mounted in a spider carried by venturi panel 34.
- the propeller fan wheel 44 is disposed within the venturi opening in panel 34 for producing an upflowing air movement through the venturi opening. Therefore, the fan draws outside air inwardly through the lower coil section'16a and blows said air outwardly through the upper coil section 16b.
- FIG. 4 arrangement is a practical form of the FIG. 2 schematic representation.
- the FIG. 4 unit embodies the advantageous operational features of the FIG. 2 unit in a desirably compact package occupying minimum space. Space economy is further achieved in that the zone below the fan wheel 44 is used to contain a conventional refrigerant compressor 48.
- Each coil lea or 1612 is initially formed in the flat, using straight heat exchange tubes 118a or 18b threaded through openings in the collars 52(FIG. 6) of the plate fins 20a or 20b.
- a mandrel is forced through each tube to expand the tube into tight mechanical bonding engagement with the fin collars.
- the headers 42 and 44 are applied to the exposed tube ends, and the fin-tube assembly is bent around arcuate forming dies to achieve the square shape of FIG. 5.
- the illustrated assembly includes flanged tube sheets 49 and 51, and intermediate bracket plates St) between selected ones of the fins as shown in FIG. 6.
- the tube sheets and bracket plates are positioned on the heat exchanger tubes as part of the fin-tube stack (prior to mandrel expansion of the fins onto the tube collars 52).
- the mandrels are forced through the tubes to expand them into tight bonding relation with the fin collars 52 they also affix the tubes to the tube sheet 49 i and 51, and the bracket plates 50.
- each bracket plate 50 is preformed with a sleeve-like extension 54.
- suitable tie bolts FIG. 6
- Suitable nuts 58 can be threaded onto the lower ends of the tie bolts to retain the assembly together.
- Tube sheets 49 and 51 may be welded together or screwed together at their facing flanges.
- FIG. 7 illustrates an alternate mechanism for securing the two heat exchange coils to the various plates 30, 34 and 32.
- each heat exchange coil can be provided with a bracket 50a having a flange foot portion 53 arranged to lie flat against the respective panel 30, 32 or 34. Suitable welding screws, etc., can be used to secure the bracket to the respective panel.
- the bracket is secured to the heat exchange coil by the tube-expansion method described in connection with FIG. 6.
- FIG. 7 shows one bracket at the lower end of a heat exchange coil 16a, but it will be appreciated that a similar bracket can be located at the upper end of each coil so that each coil can be secured at its upper and lower ends to respective ones of the panels 30, 32 and 34.
- AIR VELOCITY It is desirable that the air velocity across the fins be relatively high in order to achieve a scrubbing action on the tin edges and fan surfaces.
- a given volumetric air flow by fan 44 is accompanied by a relatively high linear velocity because the total air volume is forced through two coils in series with one another.
- the flow cross-section of each coil is only one-half that of the conventional flow through unit (FIG. 3) so that the linear velocity through each FIG. 4 coil is twice what it would be if the air was moved once through only one coil.
- the higher linear velocity means a better scrubbing action on the tin surfaces and a more effective heat transfer action.
- the air flow path is designed to be more conducive to improved heat transfer because of the superimposed relation of the two coils. Inter-surface tube temperatures from the warmer to cooler tubes (as the refrigerant gas condensing action is being performed) are not transmitted because a normal heat transfer path of migration to the cooler edge is customary.
- the low temperature cooling air first flows past the lower cooler coil where it is heated; the increased volume flow (higher cubic feet) then flows across the upper coil at a somewhat higher linear velocity.
- This invention results in improved counter flow heat transfer without inter-tube surface temperature migration, combined with an air heat rise expansion plenum area (within the unit itself) to eliminate air flow pressure hold-back (due to air heating and expanding inter-fin such as on multirow depth coils).
- the fan 44 and compressor 48 are located upstream with respect to heat exchange coil 161;. This coil therefore acts as a barrier or absorber with respect to sounds emitted by the fan and compressor. This is an advantageous feature in residential air conditioners where houses may be rather close together.
- REFRIGERANT FLOW VELOCITY As the refrigerant flows through the condenser tubes some of the refrigerant condenses before it reaches the outlet of the condenser.
- the condensed refrigerant occupies less tube cross-section than the gaseous refrigerant so that the effective passage cross-section for refrigerant gas flow increases from inlet end of the condenser to the outlet end.
- the increased refrigerant gas flow flow passage area causes a reduction in the linear flow rate of the gas near the outlet end of the condenser.
- a low gas flow rate is undesirable because it means a lesser resultant refrigerant flow tube loading, whereas the refrigerant thermal coefficient (f B.- t.u./I-Ir/sq.ft./F) is reduced.
- F IG.'10 illustrates a refrigerant flow passage arrangement which can be used to maintain a satisfactorily high refrigerant flow velocity along the length of the condenser from the inlet end to the outlet end.
- the gaseous refrigerant enters through header 42 and flows through six relatively large diameter tubes 18b to a second header 44a which connects with a subjacent header 44b. All of the refrigerant then flows through two smaller refrigerant tubes 18a to another header 42a. Condensation occuring along the lengths of the tubes 18b tends to reduce the refrigerant velocity toward the downstream ends of these tubes, but the smaller diameters of tubes 18a and/or the lesser numbers of tubes 18a tends to restore the velocity to a satisfactory level. In a similar manner the diameters of the next tubes 18a can be reduced to obtain a satisfactory flow velocity in the lower tubes.
- FIG. assembly comprising header 42, tubes 18b and header 44 forms the upper coil 16b in FIG. 4.
- the FIG. 10 assembly comprising the remaining headers and lower tubes 18a forms the lower coil 16a in FIG. 4.
- FIG. 4 shows two connected separate coils one above the other. However, it is believed possible to employ one single coil extending the entire height of the package.
- FIG. 9 fragmentarily shows a single height coil having suitable brackets 50b connected to selected heat exchange tubes, as by the tube-expansion procedure previously outlined. Each bracket projects inwardly below the venturi panel 34a. In this instance the venturi panel is provided with a downturned peripheral flange 35b fitting into a notch in each bracket 50a. In this manner it is believed possible to incorporate the venturi panel midway betweenthe top and bottom panels 30 and 32(FIG. 4) while still using only one annular coil (instead of two coils as shown in FIG. 4).
- FIG. 9 arrangement may suffer somewhat in that the venturi panel does not bisect the coil so that air exhausted from fan 44 can more easily recycle as shown by arrow 62. Such recycling is not desirable in that the recycle air is heated air that does not have quite as satisfactory a heat transfer characteristic as fresh air coming in through the blower portions of the coil.
- the compressor 48 outlet is connected to upper coil 16!; by a tube of sufficient length to dissassembly of the coil without breakage of the fluid connection.
- advantageously manual disconnect valves can be provided in the fluid connections to facilitate compressor replacement and system recharging.
- coils 16a and 16b tends to prevent easy connection of the compressor with its supply voltage and refrigerant lines.
- the dished character of panel 30 enables electrical wiring and fluid lines to be run into the interior space circumscribed by the coil, i.e., through the sidewall of the dish or surrounding land area.
- the arrangement is believed practical and adapted to fairly easy repair procedures when necessary.
- a principal feature of the invention is the coil-fan relation wherein the fan has draw-through action with respect to one section of the coil and blow-through action with respect to another section of the coil. This arrangement is believed to promote high linear air velocities and improved heat transfer operation on the air side.
- a cooperating feature of the invention is the annular character of the coil or coils which provides a large coil face area in a small volume package.
- the desirable result is achieved with a minimum quantity of non-useful dead casing wall area, since the only casing components are the three panels 30, 32 and 34.
- These panels I may be formed, at least partly, using a common die, which makes for some manufacturing economy. Suitable materials such as steel, aluminum, or plastic may be used.
- a refrigerant condenser comprising fluid connected condenser coil sections wherein each coil section is an upstanding coil of generally annular configuration in plan outline with tubes extending there around and arranged one above another and said coil sections are stacked one above the other to provide a stacked coil assembly, means at each end of the stacked coil assembly to block the-flow air through the ends of the assembly and a fan located in the space circumscribed by the coils with its axis of rotation generally extending in the direction of the axis of the stacked coil assembly and the blades of the fan located between the ends of the stacked coil assembly for drawing air into the circumscribed space through that portion of the coil assembly which extends from one end thereof to the fan blades and for blowing air from said circumscribed space through that portion of the coil assembly which extends from its other end to the fan blades.
- coil sections comprise connected refrigerant passages of which some are sized larger than others to at least partially compensate for different gas volumes handled by the respective passages.
- a refrigerant condenser comprising coil means of generally annular configuration in plan outline with tubes extending there around and arranged one above another, means at each end of the coil means for blocking the flow of air through the ends thereof, and a fan located in the space circumscribed by the coil means with its axis of rotation generally extending in the direction of the axis of the coil means and the blades of the fan located between the ends of the coil means for drawing air into the circumscribed space through that portion of the coil means which extends from one end thereof to the fan blades and for blowing air from said circumscribed space through that portion of the coil means which extends from its other end to the fan blades.
- the combination of claim 5 which includes a venthe respective passages. turi panel between opposite ends of the coil means and 8.
- the combination of claim 5 including a refrigerant has said fan blades located in the venturi opening. compressor in said circumscribed space between one 7.
- the combination of claim 6 wherein the coil end of the coil means and the fan blades. means comprises connected refrigerant passages of 9.
- the combination of claim 5 wherein the coil which some are sized larger than others to at least parmeans has a generally square planar outline. tially compensate for different gas volumes handled by LII
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- General Engineering & Computer Science (AREA)
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- Other Air-Conditioning Systems (AREA)
Abstract
Description
Claims (9)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US19187371A | 1971-10-22 | 1971-10-22 |
Publications (1)
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US3759321A true US3759321A (en) | 1973-09-18 |
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Family Applications (1)
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US00191873A Expired - Lifetime US3759321A (en) | 1971-10-22 | 1971-10-22 | Condenser coil apparatus |
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Cited By (36)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4062401A (en) * | 1976-05-03 | 1977-12-13 | International Harvester Company | Toroidal multifluid segmented heat exchanger |
US4136735A (en) * | 1975-01-24 | 1979-01-30 | International Harvester Company | Heat exchange apparatus including a toroidal-type radiator |
US4535838A (en) * | 1983-11-07 | 1985-08-20 | American Standard Inc. | Heat exchange coil and method of making |
US4664179A (en) * | 1984-06-23 | 1987-05-12 | Mitsubishi Denki Kabushiki Kaisha | Heat exchanger |
US4723419A (en) * | 1986-08-07 | 1988-02-09 | American Standard Inc. | Outdoor heat exchanger section |
JPS63112065A (en) * | 1986-10-30 | 1988-05-17 | Showa Alum Corp | Heat exchanger made of aluminum |
US4770241A (en) * | 1985-01-10 | 1988-09-13 | Carrier Corporation | Method and apparatus for forming slit fin coils |
US4967830A (en) * | 1988-05-02 | 1990-11-06 | Eubank Manufacturing Enterprises, Inc. | Arcuate tubular evaporator heat exchanger |
US5190100A (en) * | 1986-07-29 | 1993-03-02 | Showa Aluminum Corporation | Condenser for use in a car cooling system |
US5246064A (en) * | 1986-07-29 | 1993-09-21 | Showa Aluminum Corporation | Condenser for use in a car cooling system |
US5458190A (en) * | 1986-07-29 | 1995-10-17 | Showa Aluminum Corporation | Condenser |
US5482112A (en) * | 1986-07-29 | 1996-01-09 | Showa Aluminum Kabushiki Kaisha | Condenser |
US5538075A (en) * | 1988-05-02 | 1996-07-23 | Eubank Manufacturing Enterprises, Inc. | Arcuate tubular evaporator heat exchanger |
USRE35655E (en) * | 1986-07-29 | 1997-11-11 | Showa Aluminum Corporation | Condenser for use in a car cooling system |
USRE35742E (en) * | 1986-07-29 | 1998-03-17 | Showa Aluminum Corporation | Condenser for use in a car cooling system |
EP1114969A2 (en) * | 1996-02-23 | 2001-07-11 | SANYO ELECTRIC Co., Ltd. | Power controllable type air conditioner |
WO2001051859A1 (en) * | 2000-01-14 | 2001-07-19 | Toshiba Carrier Corporation | Outdoor unit of air conditioner |
US20040134638A1 (en) * | 2001-08-14 | 2004-07-15 | Berchowitz David M. | Condenser evaporator and cooling device |
US20040206107A1 (en) * | 2003-04-16 | 2004-10-21 | Min-Bon Koo | Fan assembly for refrigerator |
US20050126765A1 (en) * | 2003-12-01 | 2005-06-16 | Carlambrogio Bianchi | Bent coil for ducted unit |
US20050183450A1 (en) * | 2003-02-26 | 2005-08-25 | Lg Electronics Inc. | Built-in type outdoor unit for air conditioner |
US7104088B1 (en) * | 2005-09-22 | 2006-09-12 | Teppo K. Jokinen | Machine for improving air conditioning condenser with multiply capacities |
US20070056716A1 (en) * | 2004-09-14 | 2007-03-15 | Harry Schoell | Centrifugal condenser |
WO2008097208A2 (en) * | 2007-02-08 | 2008-08-14 | Klimasan Klima Sanayi Ve Ticaret A.S. | A condenser |
US20080223945A1 (en) * | 2007-03-12 | 2008-09-18 | Lau George H K | Heat exchanger |
US20090000146A1 (en) * | 2007-06-26 | 2009-01-01 | Gm Global Technology Operations, Inc. | Evaporator Core Drying System |
US20090084131A1 (en) * | 2007-10-01 | 2009-04-02 | Nordyne Inc. | Air Conditioning Units with Modular Heat Exchangers, Inventories, Buildings, and Methods |
WO2010091959A1 (en) * | 2009-02-13 | 2010-08-19 | BSH Bosch und Siemens Hausgeräte GmbH | Heat exchanger in particular condenser for a domestic refrigerator |
US20100326624A1 (en) * | 2009-06-26 | 2010-12-30 | Trane International Inc. | Blow Through Air Handler |
US20110168354A1 (en) * | 2008-09-30 | 2011-07-14 | Muller Industries Australia Pty Ltd. | Modular cooling system |
US20130019622A1 (en) * | 2011-07-22 | 2013-01-24 | Fujitsu General Limited | Air conditioning apparatus |
CN103221762A (en) * | 2010-11-24 | 2013-07-24 | 开利公司 | Refrigeration unit with corrosion durable heat exchanger |
EP2818346A3 (en) * | 2013-06-24 | 2015-04-01 | Dometic Sweden AB | Coolant liquefier unit for the transport of chilled goods |
US20160084579A1 (en) * | 2014-09-24 | 2016-03-24 | Raschid Alani Showole | Heat Exchanger for a Condenser Unit which Eliminate Corner and Concentric Eddies for High Energy Efficiency |
US20160258689A1 (en) * | 2015-03-03 | 2016-09-08 | Johnson Matthey Process Technologies, Inc. | Heat exchanger |
US10920998B2 (en) * | 2017-02-20 | 2021-02-16 | Mitsubishi Electric Corporation | Outdoor unit for air-conditioning apparatus |
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US3498080A (en) * | 1968-04-08 | 1970-03-03 | Carrier Corp | Apertured slidable member for air conditioners |
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US1821754A (en) * | 1930-04-22 | 1931-09-01 | Gen Electric | Air cooled condenser for refrigerating systems |
US1996927A (en) * | 1930-10-10 | 1935-04-09 | Donald W Lake | Heater |
US2610484A (en) * | 1950-01-13 | 1952-09-16 | Betz Corp | Compact refrigeration unit for cooling air |
US2662748A (en) * | 1952-07-01 | 1953-12-15 | Swingfire Bahamas Ltd | Heat exchanger with adjustable casing for varying recirculation |
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Cited By (54)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4136735A (en) * | 1975-01-24 | 1979-01-30 | International Harvester Company | Heat exchange apparatus including a toroidal-type radiator |
US4062401A (en) * | 1976-05-03 | 1977-12-13 | International Harvester Company | Toroidal multifluid segmented heat exchanger |
US4535838A (en) * | 1983-11-07 | 1985-08-20 | American Standard Inc. | Heat exchange coil and method of making |
US4664179A (en) * | 1984-06-23 | 1987-05-12 | Mitsubishi Denki Kabushiki Kaisha | Heat exchanger |
US4770241A (en) * | 1985-01-10 | 1988-09-13 | Carrier Corporation | Method and apparatus for forming slit fin coils |
USRE35711E (en) * | 1986-07-29 | 1998-01-06 | Showa Aluminum Corporation | Condenser for use in a car cooling system |
USRE35655E (en) * | 1986-07-29 | 1997-11-11 | Showa Aluminum Corporation | Condenser for use in a car cooling system |
USRE35742E (en) * | 1986-07-29 | 1998-03-17 | Showa Aluminum Corporation | Condenser for use in a car cooling system |
US5482112A (en) * | 1986-07-29 | 1996-01-09 | Showa Aluminum Kabushiki Kaisha | Condenser |
US5190100A (en) * | 1986-07-29 | 1993-03-02 | Showa Aluminum Corporation | Condenser for use in a car cooling system |
US5246064A (en) * | 1986-07-29 | 1993-09-21 | Showa Aluminum Corporation | Condenser for use in a car cooling system |
US5458190A (en) * | 1986-07-29 | 1995-10-17 | Showa Aluminum Corporation | Condenser |
US4723419A (en) * | 1986-08-07 | 1988-02-09 | American Standard Inc. | Outdoor heat exchanger section |
JPS63112065A (en) * | 1986-10-30 | 1988-05-17 | Showa Alum Corp | Heat exchanger made of aluminum |
JPH0245945B2 (en) * | 1986-10-30 | 1990-10-12 | Showa Aluminium Co Ltd | |
US4967830A (en) * | 1988-05-02 | 1990-11-06 | Eubank Manufacturing Enterprises, Inc. | Arcuate tubular evaporator heat exchanger |
US5538075A (en) * | 1988-05-02 | 1996-07-23 | Eubank Manufacturing Enterprises, Inc. | Arcuate tubular evaporator heat exchanger |
EP1114969A2 (en) * | 1996-02-23 | 2001-07-11 | SANYO ELECTRIC Co., Ltd. | Power controllable type air conditioner |
EP1114969A3 (en) * | 1996-02-23 | 2001-07-18 | SANYO ELECTRIC Co., Ltd. | Power controllable type air conditioner |
WO2001051859A1 (en) * | 2000-01-14 | 2001-07-19 | Toshiba Carrier Corporation | Outdoor unit of air conditioner |
US6591628B2 (en) | 2000-01-14 | 2003-07-15 | Toshiba Carrier Corporation | Outdoor unit of air conditioner |
US20040134638A1 (en) * | 2001-08-14 | 2004-07-15 | Berchowitz David M. | Condenser evaporator and cooling device |
US7073567B2 (en) * | 2001-08-14 | 2006-07-11 | Global Cooling Bv | Condenser evaporator and cooling device |
US20050183449A1 (en) * | 2003-02-26 | 2005-08-25 | Lg Electronics Inc. | Built-in type outdoor unit for air conditioner |
US20050183450A1 (en) * | 2003-02-26 | 2005-08-25 | Lg Electronics Inc. | Built-in type outdoor unit for air conditioner |
US6990832B2 (en) * | 2003-02-26 | 2006-01-31 | Lg Electronics Inc. | Built-in type outdoor unit for air conditioner |
US7174740B2 (en) | 2003-02-26 | 2007-02-13 | Lg Electronics. Inc. | Built-in type outdoor unit for air conditioner |
US20040206107A1 (en) * | 2003-04-16 | 2004-10-21 | Min-Bon Koo | Fan assembly for refrigerator |
US7231779B2 (en) * | 2003-04-16 | 2007-06-19 | Lg Electronics Inc. | Fan assembly for refrigerator |
US20050126765A1 (en) * | 2003-12-01 | 2005-06-16 | Carlambrogio Bianchi | Bent coil for ducted unit |
US8091376B2 (en) | 2003-12-01 | 2012-01-10 | Carrier Corporation | Bent coil for ducted unit |
US20070056716A1 (en) * | 2004-09-14 | 2007-03-15 | Harry Schoell | Centrifugal condenser |
US7798204B2 (en) * | 2004-09-14 | 2010-09-21 | Cyclone Power Technologies, Inc. | Centrifugal condenser |
US7104088B1 (en) * | 2005-09-22 | 2006-09-12 | Teppo K. Jokinen | Machine for improving air conditioning condenser with multiply capacities |
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