EP1646833A1 - Evaporator for a refrigeration appliance - Google Patents
Evaporator for a refrigeration applianceInfo
- Publication number
- EP1646833A1 EP1646833A1 EP04737715A EP04737715A EP1646833A1 EP 1646833 A1 EP1646833 A1 EP 1646833A1 EP 04737715 A EP04737715 A EP 04737715A EP 04737715 A EP04737715 A EP 04737715A EP 1646833 A1 EP1646833 A1 EP 1646833A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- evaporator
- tube
- refrigerant fluid
- transition region
- tube portions
- 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.)
- Withdrawn
Links
- 238000005057 refrigeration Methods 0.000 title claims abstract description 9
- 239000003507 refrigerant Substances 0.000 claims abstract description 32
- 239000012530 fluid Substances 0.000 claims abstract description 31
- 239000007788 liquid Substances 0.000 claims abstract description 7
- 230000007704 transition Effects 0.000 claims description 13
- 238000010276 construction Methods 0.000 description 9
- 238000004519 manufacturing process Methods 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 238000005219 brazing Methods 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 239000012808 vapor phase Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- 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
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/0071—Evaporators
Definitions
- the present invention refers to an evaporator for a refrigeration appliance, for example of the type used in a refrigeration circuit of refrigerators and freezers and other refrigeration appliances.
- the invention is particularly related to an evaporator comprising an assembly .of tubes arranged in series, through which a refrigerant fluid is forced to pass .
- evaporators known in the art use tubes made of steel, aluminum, copper or plastic material to conduct the refrigerant fluid, which exchanges heat with a secondary surface or with the air, in order to refrigerate the air in contact with the evaporator or with the loads deposited in an ambient refrigerated by said evaporator.
- evaporator constructions which utilize these tubes, such as the evaporators of the tube-fin, tube-wire, and tube-plate types.
- these evaporators are produced with a constant tube diameter.
- the internal area of the tube is selected so as to allow a good heat exchange without the refrigerant fluid flow being submitted to a high load loss, i.e., to a high pressure loss between the inlet and the outlet of the evaporator, . resulting from the attrition of the refrigerant fluid flow with the walls and from the density variation of the refrigerant fluid.
- the refrigerant fluid in the inlet contains a great amount of liquid.
- the refrigerant fluid absorbs the heat and flows through the evaporator, the liquid is progressively transformed in vapor and the volume occupied by the refrigerant fluid (its specific volume) is progressively considerably increased.
- the refrigerant fluid significantly accelerates and the high speed tends to produce a higher load loss, making the system lose efficiency.
- this diameter has to be selected so as to minimize both the load loss and the performance loss. Since the highest the amount of vapor existing in the flow (which significantly increases its speed) the higher the load loss, a constant diameter conducts to oversize part of the evaporator that contains a significant portion of refrigerant fluid in a liquid state and which flows at low speed.
- an evaporator for a refrigeration appliance comprising a tube extension presenting an inlet for the refrigerant fluid in liquid state and an outlet for the refrigerant fluid in gaseous state, said tube extension comprising at least two tube portions, arranged in series and having different diameters and which are dimensioned to guarantee, to the refrigerant fluid flow, a more uniform speed along the different tube portions, without altering the flow rate of this refrigerant fluid between the inlet and the outlet of the tube extension.
- Figure 1 is a front schematic view of the tubular development of an evaporator constructed according to the present invention
- Figure 2 is an enlarged lateral view of a possible construction for a transition region between two tube portions presenting different diameters and arranged in series;
- Figure 3 is an enlarged lateral view of another possible construction for a transition region between two tube portions presenting different diameters and arranged in series.
- the evaporator of the present invention comprises a tube extension 10, presenting an inlet 11 for the refrigerant fluid in liquid state and an outlet 12 for the refrigerant fluid in gaseous state, said tube extension 10 being formed by at least two tube portions 10a, 10b with different diameters and which are connected in series, in order to conduct a refrigerant fluid from the refrigerating system to which the evaporator is operatively associated, the different diameters being dimensioned to guarantee, to the refrigerant fluid flow, a more uniform speed along the different tube portions, without altering the flow rate of this refrigerant fluid between the inlet 11 and the outlet 12 of the tube extension 10.
- the dimensioning of the diameter for each tube portion 10a, 10b is determined so that said diameter is progressively increased as the refrigerant fluid is conducted from the inlet 11 to the outlet 12 of the tube extension 10 of the evaporator.
- connection between each two tube portions 10a, 10b arranged in series and having different diameters is made through a transition region 20, whose diameter varies between those diameters of the tube portions 10a, 10b to which it is interconnected.
- At least one transition region 20 has a diameter that varies, gradually, between the different diameters of the tube portions 10a, 10b which said transition region is interconnecting.
- at least one transition region 20 is substantially frusto-conical .
- at least one transition region is in the form of an annular tube portion, disposed orthogonal to the axis of the tube portions 10a, 10b, to which it is interconnected and determining, for example, an abrupt diameter variation between said tube portions 10a, 10b.
- the present invention provides the following benefits: reducing the refrigerant fluid load of the system, by reducing the internal volume of the evaporator; moderately increasing the speed of the refrigerant fluid in the initial regions of the evaporator, increasing heat transfer without increasing load loss thereof; improving the performance of the system as a whole .
- one of the tube portions 10a, 10b such as the one used in the first 50% of the circuit of the evaporator, from the inlet of its tube extension 10, presents a smaller internal diameter, for example of about 5.3mm, and the tube portion 10b disposed in the region of the outlet 12 of the tube extension 10 presents an internal diameter of 6mm.
- another tube portion is connected with an internal diameter, which is smaller than that of the tube portion 10a and occupying, for example, an inlet region inferior to 30% of the refrigerant circuit.
- the junction between the tube portions 10a, 10b of different diameters, or between these and the transition regions 10 which interconnect them, is made by known means, such as welding, brazing, or other type of available mechanical junction.
- the inventive concept of the present construction can be used in different evaporator constructions, such as the evaporators of the tube-fin, tube-wire and tube- plate types, by varying the diameters of the tube portions which form the tube extension of the evaporator, increasing said diameters as the refrigerant fluid flows along the circuit, changing from the liquid phase to the vapor phase.
- the construction proposed herein is particularly advantageous for the evaporators to be applied to refrigeration appliances of the "no frost" type.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Vessels And Coating Films For Discharge Lamps (AREA)
Abstract
An evaporator for a refrigeration appliance comprising a tube extension presenting an inlet (11) for the refrigerant fluid in liquid state and an outlet (12) for the refrigerant fluid in gaseous state, said tube extension (10) comprising at least two tube portions (10a, 10b) arranged in series and having different diameters which are dimensioned to guarantee, to the refrigerant fluid flow, a more uniform speed in the interior of the evaporator, without altering the flow rate of this refrigerant fluid between the inlet (11) and the outlet (12) of the tube extension (10).
Description
EVAPORATOR FOR A REFRIGERATION APPLIANCE Field of the Invention
The present invention refers to an evaporator for a refrigeration appliance, for example of the type used in a refrigeration circuit of refrigerators and freezers and other refrigeration appliances. The invention is particularly related to an evaporator comprising an assembly .of tubes arranged in series, through which a refrigerant fluid is forced to pass . Prior Art
Several evaporators known in the art use tubes made of steel, aluminum, copper or plastic material to conduct the refrigerant fluid, which exchanges heat with a secondary surface or with the air, in order to refrigerate the air in contact with the evaporator or with the loads deposited in an ambient refrigerated by said evaporator.
There are several evaporator constructions which utilize these tubes, such as the evaporators of the tube-fin, tube-wire, and tube-plate types. In order to simplify manufacture, these evaporators are produced with a constant tube diameter. The internal area of the tube is selected so as to allow a good heat exchange without the refrigerant fluid flow being submitted to a high load loss, i.e., to a high pressure loss between the inlet and the outlet of the evaporator, . resulting from the attrition of the refrigerant fluid flow with the walls and from the density variation of the refrigerant fluid. In an evaporator, the refrigerant fluid in the inlet contains a great amount of liquid. As the refrigerant fluid absorbs the heat and flows through the evaporator, the liquid is progressively transformed in vapor and the volume occupied by the refrigerant fluid (its specific volume) is progressively considerably
increased. In order to maintain the flow rate, the refrigerant fluid significantly accelerates and the high speed tends to produce a higher load loss, making the system lose efficiency. When a constant tube diameter is used, this diameter has to be selected so as to minimize both the load loss and the performance loss. Since the highest the amount of vapor existing in the flow (which significantly increases its speed) the higher the load loss, a constant diameter conducts to oversize part of the evaporator that contains a significant portion of refrigerant fluid in a liquid state and which flows at low speed. Objects of the Invention By reason of the disadvantages mentioned above, it is an object of the present invention to provide an evaporator of low cost and which presents less load loss and better performance. Summary of the Invention This and other objects of the present invention are achieved through an evaporator for a refrigeration appliance, comprising a tube extension presenting an inlet for the refrigerant fluid in liquid state and an outlet for the refrigerant fluid in gaseous state, said tube extension comprising at least two tube portions, arranged in series and having different diameters and which are dimensioned to guarantee, to the refrigerant fluid flow, a more uniform speed along the different tube portions, without altering the flow rate of this refrigerant fluid between the inlet and the outlet of the tube extension. Brief Description of the Drawings
The invention will be described below, with reference to the enclosed drawings, in which: Figure 1 is a front schematic view of the tubular
development of an evaporator constructed according to the present invention;
Figure 2 is an enlarged lateral view of a possible construction for a transition region between two tube portions presenting different diameters and arranged in series; and
Figure 3 is an enlarged lateral view of another possible construction for a transition region between two tube portions presenting different diameters and arranged in series.
Description of the Illustrated Embodiment In order to comply with the proposed objects, the evaporator of the present invention comprises a tube extension 10, presenting an inlet 11 for the refrigerant fluid in liquid state and an outlet 12 for the refrigerant fluid in gaseous state, said tube extension 10 being formed by at least two tube portions 10a, 10b with different diameters and which are connected in series, in order to conduct a refrigerant fluid from the refrigerating system to which the evaporator is operatively associated, the different diameters being dimensioned to guarantee, to the refrigerant fluid flow, a more uniform speed along the different tube portions, without altering the flow rate of this refrigerant fluid between the inlet 11 and the outlet 12 of the tube extension 10. The dimensioning of the diameter for each tube portion 10a, 10b is determined so that said diameter is progressively increased as the refrigerant fluid is conducted from the inlet 11 to the outlet 12 of the tube extension 10 of the evaporator.
According to the present invention, the connection between each two tube portions 10a, 10b arranged in series and having different diameters is made through a transition region 20, whose diameter varies between
those diameters of the tube portions 10a, 10b to which it is interconnected.
In a constructive alternative, at least one transition region 20 has a diameter that varies, gradually, between the different diameters of the tube portions 10a, 10b which said transition region is interconnecting. In a constructive option of this alternative illustrated in figure 2, at least one transition region 20 is substantially frusto-conical . In another constructive alternative illustrated in figure 3, at least one transition region is in the form of an annular tube portion, disposed orthogonal to the axis of the tube portions 10a, 10b, to which it is interconnected and determining, for example, an abrupt diameter variation between said tube portions 10a, 10b.
The utilization of two or more diameters for different tube portions in the construction of these evaporators allows reducing the production cost of the evaporator, improving the performance thereof.
The present invention provides the following benefits: reducing the refrigerant fluid load of the system, by reducing the internal volume of the evaporator; moderately increasing the speed of the refrigerant fluid in the initial regions of the evaporator, increasing heat transfer without increasing load loss thereof; improving the performance of the system as a whole . In a constructive option, one of the tube portions 10a, 10b, such as the one used in the first 50% of the circuit of the evaporator, from the inlet of its tube extension 10, presents a smaller internal diameter, for example of about 5.3mm, and the tube portion 10b disposed in the region of the outlet 12 of the tube extension 10 presents an internal diameter of 6mm.
In another exemplificative construction (not illustrated), adjacent to the inlet 11 of the tube extension 10 and in front of the tube portion 10a, another tube portion is connected with an internal diameter, which is smaller than that of the tube portion 10a and occupying, for example, an inlet region inferior to 30% of the refrigerant circuit. In any of the possible constructions, the junction between the tube portions 10a, 10b of different diameters, or between these and the transition regions 10 which interconnect them, is made by known means, such as welding, brazing, or other type of available mechanical junction. The inventive concept of the present construction can be used in different evaporator constructions, such as the evaporators of the tube-fin, tube-wire and tube- plate types, by varying the diameters of the tube portions which form the tube extension of the evaporator, increasing said diameters as the refrigerant fluid flows along the circuit, changing from the liquid phase to the vapor phase. The construction proposed herein is particularly advantageous for the evaporators to be applied to refrigeration appliances of the "no frost" type.
Claims
1. An evaporator for a refrigeration appliance comprising a tube extension presenting an inlet (11) for the refrigerant fluid in liquid state and an outlet (12) for the refrigerant fluid in gaseous state, characterized in that said tube extension (10) comprises at least two tube portions (10a, 10b) arranged in series and having different diameters, which are dimensioned so as to guarantee, to the refrigerant fluid flow, a more uniform speed along the different tube portions, without altering the flow rate of this refrigerant fluid between the inlet (11) and the outlet (12) of the tube extension (10) .
2. The evaporator as set forth in claim 1, characterized in that it comprises a transition region (20) interconnecting each two tube portions (10a, 10b) of different diameters and arranged in series.
3. The evaporator as set forth in claim 2, characterized in that the transition region (20) has a diameter that varies between the diameters of the tube portions (10a, 10b) to which it is interconnected.
4. The evaporator as set forth in claim 2 , characterized in that the transition region (20) has a diameter that varies gradually.
5. The evaporator as set forth in claim 4, characterized in that the transition region (20) is substantially frusto-conical .
6. The evaporator as set forth in claim 2, characterized in that the transition region (20) is an annular tube portion, disposed orthogonal to the axis of the tube portions (10a, 10b) to which it is interconnected.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
BR0303172-1A BR0303172A (en) | 2003-07-21 | 2003-07-21 | Evaporator for refrigerator |
PCT/BR2004/000121 WO2005008152A1 (en) | 2003-07-21 | 2004-07-19 | Evaporator for a refrigeration appliance |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1646833A1 true EP1646833A1 (en) | 2006-04-19 |
Family
ID=36642325
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04737715A Withdrawn EP1646833A1 (en) | 2003-07-21 | 2004-07-19 | Evaporator for a refrigeration appliance |
Country Status (7)
Country | Link |
---|---|
US (1) | US20060225460A1 (en) |
EP (1) | EP1646833A1 (en) |
KR (1) | KR20060111447A (en) |
AU (1) | AU2004257307A1 (en) |
BR (1) | BR0303172A (en) |
MX (1) | MXPA06000920A (en) |
WO (1) | WO2005008152A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
TWI349092B (en) * | 2008-09-22 | 2011-09-21 | Ind Tech Res Inst | Cooling system and evaporator thereof |
US8646286B2 (en) * | 2010-12-30 | 2014-02-11 | Pdx Technologies Llc | Refrigeration system controlled by refrigerant quality within evaporator |
CN103225940B (en) * | 2013-04-27 | 2016-08-10 | 合肥美的电冰箱有限公司 | Refrigerator and evaporator thereof |
KR101461057B1 (en) * | 2014-04-02 | 2014-11-20 | 윤재동 | Apparatus for cooling and heating with one circulating loop using thermoelectric element |
DE102016102690A1 (en) * | 2016-02-16 | 2017-08-17 | Miele & Cie. Kg | Heat exchanger for a refrigerant circuit of a heat pump for a household appliance and heat pump for a household appliance |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003240472A (en) * | 2002-02-20 | 2003-08-27 | Daikin Ind Ltd | Heat exchanger, method of manufacturing heat exchanger, and air conditioner |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2702993A (en) * | 1951-07-24 | 1955-03-01 | Int Harvester Co | Hermetic connector |
US3531947A (en) * | 1968-10-29 | 1970-10-06 | Gen Electric | Refrigeration system including refrigerant noise suppression |
GB1286446A (en) * | 1970-01-30 | 1972-08-23 | Johannes Burmester & Co | Plate heat exchanger |
DE2548240A1 (en) * | 1975-10-28 | 1977-05-12 | Linde Ag | Cooling system employing expansion in nozzles - has part of compressed refrigerant medium expanded and used to cool down remaining refrigerant |
US4150558A (en) * | 1977-11-04 | 1979-04-24 | General Electric Company | Method for forming a variable restrictor |
JPS5773392A (en) * | 1980-10-22 | 1982-05-08 | Hitachi Ltd | Corrugated fin type heat exchanger |
US4408467A (en) * | 1981-11-23 | 1983-10-11 | Carrier Corporation | Noise suppressing feeder tube for a refrigerant circuit |
JPS60200089A (en) * | 1984-03-23 | 1985-10-09 | Hitachi Ltd | Direct expansion type regenerative heat exchanger |
JPS63131989A (en) * | 1986-11-21 | 1988-06-03 | Fujitsu General Ltd | Heat exchanger |
US4995453A (en) * | 1989-07-05 | 1991-02-26 | Signet Systems, Inc. | Multiple tube diameter heat exchanger circuit |
JPH07103609A (en) * | 1993-10-01 | 1995-04-18 | Nippondenso Co Ltd | Heat exchanger for freezing cycle |
US5755188A (en) * | 1995-05-04 | 1998-05-26 | The Babcock & Wilcox Company | Variable pressure once-through steam generator furnace having all welded spiral to vertical tube transition with non-split flow circuitry |
US5910166A (en) * | 1997-11-25 | 1999-06-08 | Whirlpool Corporation | Refrigeration system and a capillary tube thereof |
WO1999031444A1 (en) * | 1997-12-16 | 1999-06-24 | Matsushita Electric Industrial Co., Ltd. | Airconditioner using inflammable refrigerant |
US6557372B1 (en) * | 2002-01-28 | 2003-05-06 | Smc Kabushiki Kaisha | Refrigerating unit having plural air cooled condensers |
-
2003
- 2003-07-21 BR BR0303172-1A patent/BR0303172A/en not_active IP Right Cessation
-
2004
- 2004-07-19 EP EP04737715A patent/EP1646833A1/en not_active Withdrawn
- 2004-07-19 MX MXPA06000920A patent/MXPA06000920A/en unknown
- 2004-07-19 WO PCT/BR2004/000121 patent/WO2005008152A1/en not_active Application Discontinuation
- 2004-07-19 KR KR1020067001369A patent/KR20060111447A/en not_active Application Discontinuation
- 2004-07-19 AU AU2004257307A patent/AU2004257307A1/en not_active Abandoned
- 2004-07-19 US US10/565,391 patent/US20060225460A1/en not_active Abandoned
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003240472A (en) * | 2002-02-20 | 2003-08-27 | Daikin Ind Ltd | Heat exchanger, method of manufacturing heat exchanger, and air conditioner |
EP1486748A1 (en) * | 2002-02-20 | 2004-12-15 | Daikin Industries, Ltd. | Heat exchanger, heat exchanger manufacturing method, and air conditioner |
Also Published As
Publication number | Publication date |
---|---|
AU2004257307A1 (en) | 2005-01-27 |
US20060225460A1 (en) | 2006-10-12 |
MXPA06000920A (en) | 2006-03-30 |
WO2005008152A1 (en) | 2005-01-27 |
BR0303172A (en) | 2005-04-05 |
KR20060111447A (en) | 2006-10-27 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
AU2002238890B2 (en) | Layered heat exchanger, layered evaporator for motor vehicle air conditioners and refrigeration system | |
EP1797378B1 (en) | Refrigerant distribution device and method | |
TW541411B (en) | Condenser of sub-cool type | |
US9546824B2 (en) | Heat exchanger | |
JP3627382B2 (en) | Refrigerant condensing device and refrigerant condenser | |
US20140158332A1 (en) | Heat exchanger | |
US20120103581A1 (en) | Header unit and heat exchanger having the same | |
AU2002238890A1 (en) | Layered heat exchanger, layered evaporator for motor vehicle air conditioners and refrigeration system | |
JP2002130866A (en) | Condenser for air conditioning | |
US20110061845A1 (en) | Heat exchanger | |
JP4069804B2 (en) | Condenser with integrated heat exchanger and receiver | |
US20060225460A1 (en) | Evaporator for a refrigeration appliance | |
JP2001174103A (en) | Refrigerant condenser | |
KR100549063B1 (en) | Refrigerator | |
US20070151718A1 (en) | Fin-tube heat exchanger | |
WO2016173790A1 (en) | Cooling device comprising a condenser used in two independent refrigeration cycles | |
KR100654178B1 (en) | Method for making a decision receiver dryer's volume and condenser and receiver dryer having the volume by it in one united body | |
CN1090743C (en) | Refrigerating unit | |
US6497115B1 (en) | Evaporator and refrigerator | |
WO2018093764A1 (en) | Hybrid heat exchanger | |
KR20010109617A (en) | Condenser enhanced heat transfer performance | |
WO2021214849A1 (en) | Air conditioner, freezer, and distributor | |
JP2001227844A (en) | Condenser | |
US20020184912A1 (en) | Method for reinforcing condensation and a device thereof | |
JP2000356436A (en) | Condenser |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20060120 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE ES FR GB IT PL |
|
DAX | Request for extension of the european patent (deleted) | ||
RBV | Designated contracting states (corrected) |
Designated state(s): DE ES FR GB IT PL |
|
17Q | First examination report despatched |
Effective date: 20060509 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
18D | Application deemed to be withdrawn |
Effective date: 20071023 |