US20080190122A1 - Accumulator Integration with Heat Exchanger Header - Google Patents
Accumulator Integration with Heat Exchanger Header Download PDFInfo
- Publication number
- US20080190122A1 US20080190122A1 US11/908,450 US90845007A US2008190122A1 US 20080190122 A1 US20080190122 A1 US 20080190122A1 US 90845007 A US90845007 A US 90845007A US 2008190122 A1 US2008190122 A1 US 2008190122A1
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- United States
- Prior art keywords
- refrigerant
- heat exchanger
- accumulator
- compressor
- zone
- 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
- 230000010354 integration Effects 0.000 title 1
- 239000003507 refrigerant Substances 0.000 claims abstract description 57
- 239000007788 liquid Substances 0.000 claims abstract description 22
- 238000005057 refrigeration Methods 0.000 claims abstract description 7
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 6
- 238000000034 method Methods 0.000 claims description 7
- 235000013361 beverage Nutrition 0.000 claims 1
- 238000001816 cooling Methods 0.000 claims 1
- 238000000926 separation method Methods 0.000 claims 1
- 230000006835 compression Effects 0.000 description 10
- 238000007906 compression Methods 0.000 description 10
- 239000012808 vapor phase Substances 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 230000000873 masking effect Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000005514 two-phase flow Effects 0.000 description 1
Images
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
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two 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
- 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
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
-
- 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
-
- 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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- 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
- F25B2500/18—Optimization, e.g. high integration of refrigeration components
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
Definitions
- FIG. 1 shows a prior art vapor compression system having a compressor 1 , a gas cooler 2 , an expansion device 3 , and an evaporator 4 .
- evaporator 4 refrigerant passes through a series of heat exchanger tubes 5 in a heat exchange relationship with air being cooled as desired.
- Refrigerants typically enters tubes 5 through a header 6 and exits tubes 5 into a header 7 .
- Refrigerant collected in header 7 then flows to an accumulator 8 where liquid phase refrigerant and oil separate from vapor phase refrigerant, and vapor is drawn back to compressor 1 .
- FIG. 1 While the system illustrated in FIG. 1 is functional, as set forth above, a functional system which occupies less space is desirable.
- a refrigeration system which includes a compressor for driving a refrigerant along a flow path in at least a first mode of system operation; a first heat exchanger along the flow path downstream of the compressor in the first mode; a second heat exchanger along the flow path upstream of the compressor in the first mode; and an expansion device in the flow path downstream of the first heat exchanger and upstream of the second heat exchanger in the first mode, wherein the second heat exchanger includes a combined header and accumulator for collecting liquid and vapor refrigerant.
- the combined header and accumulator serves to conserve space which is particularly advantageous, for example in transcritical vapor compression systems.
- a method for operating a refrigeration system in accordance with the present invention comprises operating a compressor to drive a refrigerant along a flow path, sequentially, to a first heat exchanger, an expansion device, a second heat exchanger, a combined header and accumulator, and back to the compressor, wherein flow is directly from the second heat exchanger to the combined header and accumulator, and wherein flow is directly from the combined header and accumulator to the compressor.
- FIG. 1 is an illustration of a prior art vapor compression system
- FIG. 2 is a schematic illustration of a system having a combined accumulator and header according to the invention
- FIG. 3 is a schematic illustration of an alternative embodiment of the combined accumulator and header according to the invention.
- FIG. 4 is a schematic illustration of a further alternative embodiment of the combined accumulator and header in accordance with the present invention.
- the invention relates to a heat exchanger configuration for a vapor compression system and, more particularly, to a space-saving combination of the refrigerant accumulator and the heat exchanger header in a transcritical vapor compression cycle.
- heat rejection occurs at a pressure above the critical pressure of the refrigerant. During the heat rejection the refrigerant does not condense.
- the charge management in a transcritical system is usually accomplished by adding an accumulator to the evaporator outlet, following an outlet header (See FIG. 1 ).
- FIG. 2 shows the vapor compression system 10 in accordance with the present invention which includes a compressor 12 , a first heat exchanger or gas cooler 14 , an expansion device 16 and a second heat exchanger or evaporator 18 .
- evaporator 18 includes an inlet header 20 as in conventional devices, but that evaporator 18 also includes a combined header and accumulator 22 which combines the functions of separate outlet header 7 and accumulator 8 as illustrated in FIG. 1 . This advantageously allows for conservation of space while providing the desired functions of both the header and the accumulator of this device.
- combined header and accumulator 22 in accordance with the present invention is a single chamber which defines a lower liquid refrigerant zone 24 and an upper vapor refrigerant zone 26 .
- FIG. 2 shows lower liquid refrigerant zone 24 defined at a location which is lower than the inlet from the lower most tube 30 . This advantageously prevents masking and/or back-flow of liquid refrigerant with respect to lower most tube 30 .
- this chamber is defined by side, front, back, top and bottom walls around the end of the heat exchanger tubes.
- combined header and accumulator 22 advantageously has an inner conduit 32 which extends from a bottom surface of combined accumulator and header 22 upwardly above the expected liquid level of liquid within lower liquid refrigerant zone 24 .
- Compressor 12 draws vapor phase refrigerant out of vapor refrigerant zone 26 and through conduit 32 to the compressor suction line.
- a lower portion 34 of conduit 32 is preferably provided with a pin hole 36 which advantageously allows oil within the lower liquid refrigerant zone 24 to be drawn back to compressor 12 as desired.
- the heat exchangers 14 , 18 of the present invention can be provided as any known type of heat exchanger, preferably as refrigerant-air heat exchangers.
- suitable heat exchangers include but are not limited to wire on tube heat exchangers, fin heat exchangers, and the like.
- the system of the present invention is particularly well suited to a transcritical vapor compression system, for example, a system which uses CO 2 as working fluid.
- a transcritical vapor compression system for example, a system which uses CO 2 as working fluid.
- other refrigerants particularly those with similar properties to CO 2 under expected operating conditions, can be used and are considered to be well within the broad scope of the present invention.
- Expansion device 16 can be any suitable expansion device known to a person of skill in the art.
- a pressure regulator for example a pressure regulator such as that disclosed in commonly owned and simultaneously filed PCT Application bearing attorney docket number 05-258-WO and entitled HIGH SIDE PRESSURE REGULATION FOR TRANSCRITICAL VAPOR COMPRESSION SYSTEM, is also well within the scope of the present invention and is considered to be an expansion device as used herein.
- Header and accumulator 22 can advantageously be incorporated into heat exchanger 18 as shown in FIG. 2 .
- header and accumulator 22 can be a separate structure defining a chamber and communicated with heat exchanger 18 , preferably through direct flow from tubes of the heat exchanger into the chamber.
- FIG. 3 shows a further alternative embodiment of the present invention, having the same basic components as the embodiment of FIG. 2 .
- evaporator 18 is divided into two components 38 , 40 , and combined header and accumulator 22 is connected to each component 38 , 40 through a short flow conduit 42 .
- Conduit 42 is preferably very short, most preferably having a length of less than about 5 inches.
- FIG. 4 shows a further embodiment of the present invention, wherein system 10 includes the same components as those described in connection with FIGS. 2 and 3 .
- refrigerant fed from expansion device 16 to evaporator 18 flows through a single conduit 48 to combined header and accumulator 22 in accordance with the present invention. From this point, vapor phase refrigerant is drawn back to compressor 12 as desired.
- Embodiments of the invention as indicated in FIGS. 2-4 of the present invention integrate the accumulator and the evaporator outlet header into a single chamber.
- This single chamber performs the function of both the header and accumulator of the conventional system of FIG. 1 .
- the functions normally performed in the separate header and accumulator are now performed in the same space. This design reduces the space requirements for the accumulator as well as the overall tubing length and the number of tube connections.
- Two-phase flow leaving the evaporator is separated in the header.
- the liquid refrigerant is collected by gravity at the bottom of the accumulator-header.
- the vapor leaves the accumulator header through the tube inserted into the header.
- the tube has a pin-hole in the accumulator section of the header to allow oil return to the compressor.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Air-Conditioning For Vehicles (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
- This application claims the benefit of the filing date of earlier filed Provisional Application Ser. No. 60/663,911 filed Mar. 18, 2005. Further, copending application docket 05-258-WO, entitled HIGH SIDE PRESSURE REGULATION FOR TRANSCRITICAL VAPOR COMPRESSION SYSTEM and filed on even date herewith, and the aforesaid Provisional Application Ser. No. 60/663,911 disclose prior art and inventive cooler systems. The disclosure of said application is incorporated by reference herein as if set forth at length.
- In many refrigeration applications space is a limited resource. Any reduction in space requirements for the refrigeration system application can improve the overall design of the system—either by reducing the overall size or by utilizing the space that becomes available for other purposes, such as increased heat exchanger area. Thus, a consolidated component design can reduce system cost and increase system performance.
-
FIG. 1 shows a prior art vapor compression system having a compressor 1, a gas cooler 2, anexpansion device 3, and an evaporator 4. In evaporator 4, refrigerant passes through a series ofheat exchanger tubes 5 in a heat exchange relationship with air being cooled as desired. Refrigerants typically enterstubes 5 through aheader 6 andexits tubes 5 into aheader 7. Refrigerant collected inheader 7 then flows to anaccumulator 8 where liquid phase refrigerant and oil separate from vapor phase refrigerant, and vapor is drawn back to compressor 1. - While the system illustrated in
FIG. 1 is functional, as set forth above, a functional system which occupies less space is desirable. - It is therefore the primary object of the present invention to provide such a system.
- Other objects and advantages will appear herein.
- A refrigeration system is provided which includes a compressor for driving a refrigerant along a flow path in at least a first mode of system operation; a first heat exchanger along the flow path downstream of the compressor in the first mode; a second heat exchanger along the flow path upstream of the compressor in the first mode; and an expansion device in the flow path downstream of the first heat exchanger and upstream of the second heat exchanger in the first mode, wherein the second heat exchanger includes a combined header and accumulator for collecting liquid and vapor refrigerant. The combined header and accumulator serves to conserve space which is particularly advantageous, for example in transcritical vapor compression systems.
- A method is also provided for operating a refrigeration system in accordance with the present invention, which method comprises operating a compressor to drive a refrigerant along a flow path, sequentially, to a first heat exchanger, an expansion device, a second heat exchanger, a combined header and accumulator, and back to the compressor, wherein flow is directly from the second heat exchanger to the combined header and accumulator, and wherein flow is directly from the combined header and accumulator to the compressor.
- A detailed description of preferred embodiments of the present invention follows, with reference to the attached drawings, wherein:
-
FIG. 1 is an illustration of a prior art vapor compression system; -
FIG. 2 is a schematic illustration of a system having a combined accumulator and header according to the invention; -
FIG. 3 is a schematic illustration of an alternative embodiment of the combined accumulator and header according to the invention; and -
FIG. 4 is a schematic illustration of a further alternative embodiment of the combined accumulator and header in accordance with the present invention. - The invention relates to a heat exchanger configuration for a vapor compression system and, more particularly, to a space-saving combination of the refrigerant accumulator and the heat exchanger header in a transcritical vapor compression cycle. In transcritical vapor compression systems, heat rejection occurs at a pressure above the critical pressure of the refrigerant. During the heat rejection the refrigerant does not condense. The charge management in a transcritical system is usually accomplished by adding an accumulator to the evaporator outlet, following an outlet header (See
FIG. 1 ). -
FIG. 2 shows thevapor compression system 10 in accordance with the present invention which includes acompressor 12, a first heat exchanger orgas cooler 14, anexpansion device 16 and a second heat exchanger orevaporator 18. As compared toFIG. 1 , it should be readily appreciated thatevaporator 18 includes aninlet header 20 as in conventional devices, but thatevaporator 18 also includes a combined header andaccumulator 22 which combines the functions ofseparate outlet header 7 andaccumulator 8 as illustrated inFIG. 1 . This advantageously allows for conservation of space while providing the desired functions of both the header and the accumulator of this device. - As shown in
FIG. 2 , combined header andaccumulator 22 in accordance with the present invention is a single chamber which defines a lowerliquid refrigerant zone 24 and an uppervapor refrigerant zone 26. Flow enters the combined header andaccumulator 22 directly fromtubes 28 ofsecond heat exchanger 18. In this regard, it is noted thatFIG. 2 shows lowerliquid refrigerant zone 24 defined at a location which is lower than the inlet from the lowermost tube 30. This advantageously prevents masking and/or back-flow of liquid refrigerant with respect to lowermost tube 30. As shown inFIG. 2 , this chamber is defined by side, front, back, top and bottom walls around the end of the heat exchanger tubes. - Also as shown in
FIG. 2 , combined header andaccumulator 22 advantageously has aninner conduit 32 which extends from a bottom surface of combined accumulator andheader 22 upwardly above the expected liquid level of liquid within lowerliquid refrigerant zone 24.Compressor 12 draws vapor phase refrigerant out ofvapor refrigerant zone 26 and throughconduit 32 to the compressor suction line. - A
lower portion 34 ofconduit 32 is preferably provided with apin hole 36 which advantageously allows oil within the lowerliquid refrigerant zone 24 to be drawn back tocompressor 12 as desired. - The
heat exchangers - The system of the present invention is particularly well suited to a transcritical vapor compression system, for example, a system which uses CO2 as working fluid. Of course, other refrigerants, particularly those with similar properties to CO2 under expected operating conditions, can be used and are considered to be well within the broad scope of the present invention.
-
Expansion device 16 can be any suitable expansion device known to a person of skill in the art. A pressure regulator, for example a pressure regulator such as that disclosed in commonly owned and simultaneously filed PCT Application bearing attorney docket number 05-258-WO and entitled HIGH SIDE PRESSURE REGULATION FOR TRANSCRITICAL VAPOR COMPRESSION SYSTEM, is also well within the scope of the present invention and is considered to be an expansion device as used herein. - Header and
accumulator 22 can advantageously be incorporated intoheat exchanger 18 as shown inFIG. 2 . Alternatively, header andaccumulator 22 can be a separate structure defining a chamber and communicated withheat exchanger 18, preferably through direct flow from tubes of the heat exchanger into the chamber. -
FIG. 3 shows a further alternative embodiment of the present invention, having the same basic components as the embodiment ofFIG. 2 . In the embodiment ofFIG. 3 ,evaporator 18 is divided into twocomponents 38, 40, and combined header andaccumulator 22 is connected to eachcomponent 38, 40 through a short flow conduit 42. In this embodiment, it should be noted that by positioning lowermost tube 30 sufficiently high onsecond heat exchanger 18, the lowerliquid refrigerant zone 24 can be defined within combined accumulator andheader 22 so that abottom surface 44 of combined accumulator andheader 22 does not extend substantially beyond a bottom surface 46 ofsecond heat exchanger 18. Conduit 42 is preferably very short, most preferably having a length of less than about 5 inches. -
FIG. 4 shows a further embodiment of the present invention, whereinsystem 10 includes the same components as those described in connection withFIGS. 2 and 3 . With the embodiment ofFIG. 4 , refrigerant fed fromexpansion device 16 toevaporator 18 flows through a single conduit 48 to combined header andaccumulator 22 in accordance with the present invention. From this point, vapor phase refrigerant is drawn back tocompressor 12 as desired. - Embodiments of the invention as indicated in
FIGS. 2-4 of the present invention integrate the accumulator and the evaporator outlet header into a single chamber. This single chamber performs the function of both the header and accumulator of the conventional system ofFIG. 1 . Advantageously, the functions normally performed in the separate header and accumulator are now performed in the same space. This design reduces the space requirements for the accumulator as well as the overall tubing length and the number of tube connections. - Two-phase flow leaving the evaporator is separated in the header. The liquid refrigerant is collected by gravity at the bottom of the accumulator-header. The vapor leaves the accumulator header through the tube inserted into the header. The tube has a pin-hole in the accumulator section of the header to allow oil return to the compressor.
- One or more embodiments of the present invention have been described. Nevertheless, it will be understood that various modifications may be made without departing from the spirit and scope of the invention. For example, when implemented as a remanufacturing of an existing system or reengineering of an existing system configuration, details of the existing configuration may influence details of the implementation. Accordingly, other embodiments are within the scope of the following claims.
Claims (16)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US11/908,450 US20080190122A1 (en) | 2005-03-18 | 2005-12-30 | Accumulator Integration with Heat Exchanger Header |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US66391105P | 2005-03-18 | 2005-03-18 | |
US11/908,450 US20080190122A1 (en) | 2005-03-18 | 2005-12-30 | Accumulator Integration with Heat Exchanger Header |
PCT/US2005/047574 WO2006101569A2 (en) | 2005-03-18 | 2005-12-30 | Accumulator integration with exchanger header |
Publications (1)
Publication Number | Publication Date |
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US20080190122A1 true US20080190122A1 (en) | 2008-08-14 |
Family
ID=37024268
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/908,450 Abandoned US20080190122A1 (en) | 2005-03-18 | 2005-12-30 | Accumulator Integration with Heat Exchanger Header |
Country Status (5)
Country | Link |
---|---|
US (1) | US20080190122A1 (en) |
EP (1) | EP1864059A2 (en) |
JP (1) | JP2008533430A (en) |
CN (1) | CN101203720A (en) |
WO (1) | WO2006101569A2 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012210180A1 (en) * | 2012-06-18 | 2013-12-19 | Denso Automotive Deutschland Gmbh | Method for cooling coolant of refrigerant circuit of waste heat producing device by e.g. liquid refrigerant in hybrid car, involves transferring heat between coolants and refrigerant of circuits at or in accumulator of one of circuits |
US20180094842A1 (en) * | 2016-10-05 | 2018-04-05 | Johnson Controls Technology Company | Combined suction header and accumulator unit |
IT201900003427A1 (en) * | 2019-03-08 | 2020-09-08 | Lu Ve Spa | INTAKE MANIFOLD WITH UPWARD OUTLET FOR EVAPORATORS OF REFRIGERATION SYSTEMS. |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2132500A2 (en) * | 2007-04-05 | 2009-12-16 | Johnson Controls Technology Company | Heat exchanger |
US9062900B2 (en) * | 2010-11-08 | 2015-06-23 | Honeywell International Inc. | Integrated evaporator and accumulator for refrigerant systems |
KR101902017B1 (en) * | 2011-11-18 | 2018-09-27 | 엘지전자 주식회사 | A heat exchanger and a manufacturing method the same |
CN102679633A (en) * | 2012-04-27 | 2012-09-19 | 镇江新梦溪能源科技有限公司 | Grid evaporator |
JP5772904B2 (en) * | 2013-09-02 | 2015-09-02 | ダイキン工業株式会社 | Heat recovery type refrigeration system |
JP6805473B2 (en) * | 2017-01-31 | 2020-12-23 | 荏原冷熱システム株式会社 | Absorption chiller |
WO2019097614A1 (en) * | 2017-11-15 | 2019-05-23 | 三菱電機株式会社 | Outdoor unit of air conditioner |
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---|---|---|---|---|
US2367340A (en) * | 1940-02-17 | 1945-01-16 | Chill Quick Corp | Cooling system |
US4794765A (en) * | 1987-03-27 | 1989-01-03 | Carella Thomas J | Integral evaporator and accumulator for air conditioning system |
US5505060A (en) * | 1994-09-23 | 1996-04-09 | Kozinski; Richard C. | Integral evaporator and suction accumulator for air conditioning system utilizing refrigerant recirculation |
US20030200763A1 (en) * | 2002-04-26 | 2003-10-30 | Hirotsugu Takeuchi | Vehicle air conditioner with vapor-compression refrigerant cycle |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS5513350U (en) * | 1978-07-14 | 1980-01-28 | ||
US6155075A (en) * | 1999-03-18 | 2000-12-05 | Lennox Manufacturing Inc. | Evaporator with enhanced refrigerant distribution |
-
2005
- 2005-12-30 CN CNA2005800491549A patent/CN101203720A/en active Pending
- 2005-12-30 WO PCT/US2005/047574 patent/WO2006101569A2/en active Search and Examination
- 2005-12-30 JP JP2008501868A patent/JP2008533430A/en active Pending
- 2005-12-30 US US11/908,450 patent/US20080190122A1/en not_active Abandoned
- 2005-12-30 EP EP05856047A patent/EP1864059A2/en not_active Withdrawn
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2367340A (en) * | 1940-02-17 | 1945-01-16 | Chill Quick Corp | Cooling system |
US4794765A (en) * | 1987-03-27 | 1989-01-03 | Carella Thomas J | Integral evaporator and accumulator for air conditioning system |
US5505060A (en) * | 1994-09-23 | 1996-04-09 | Kozinski; Richard C. | Integral evaporator and suction accumulator for air conditioning system utilizing refrigerant recirculation |
US20030200763A1 (en) * | 2002-04-26 | 2003-10-30 | Hirotsugu Takeuchi | Vehicle air conditioner with vapor-compression refrigerant cycle |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012210180A1 (en) * | 2012-06-18 | 2013-12-19 | Denso Automotive Deutschland Gmbh | Method for cooling coolant of refrigerant circuit of waste heat producing device by e.g. liquid refrigerant in hybrid car, involves transferring heat between coolants and refrigerant of circuits at or in accumulator of one of circuits |
US20180094842A1 (en) * | 2016-10-05 | 2018-04-05 | Johnson Controls Technology Company | Combined suction header and accumulator unit |
US10323869B2 (en) * | 2016-10-05 | 2019-06-18 | Johnson Control Technology Company | Combined suction header and accumulator unit |
IT201900003427A1 (en) * | 2019-03-08 | 2020-09-08 | Lu Ve Spa | INTAKE MANIFOLD WITH UPWARD OUTLET FOR EVAPORATORS OF REFRIGERATION SYSTEMS. |
EP3705813A1 (en) * | 2019-03-08 | 2020-09-09 | Lu-Ve S.P.A. | Suction header with upward facing outlet for evaporators of refrigeration systems |
Also Published As
Publication number | Publication date |
---|---|
WO2006101569A3 (en) | 2007-12-06 |
EP1864059A2 (en) | 2007-12-12 |
WO2006101569A2 (en) | 2006-09-28 |
CN101203720A (en) | 2008-06-18 |
JP2008533430A (en) | 2008-08-21 |
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Owner name: CARRIER COMMERCIAL REFRIGERATION, INC., NORTH CARO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HUFF, HANS-JOACHIM;SIENEL, TOBIAS H.;CHEN, YU;AND OTHERS;REEL/FRAME:017248/0915;SIGNING DATES FROM 20060201 TO 20060202 Owner name: CARRIER COMMERCIAL REFRIGERATION, INC., NORTH CARO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HUFF, HANS-JOACHIM;SIENEL, TOBIAS H.;CHEN, YU;AND OTHERS;SIGNING DATES FROM 20060201 TO 20060202;REEL/FRAME:017248/0915 |
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Owner name: CARRIER COMMERCIAL REFRIGERATION, INC., NORTH CARO Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE CORRECTIVE ASSIGNMENT TO RE-RECORD ASSIGNMENT TO CORRECT DOCKET NUMBER AND ATTACHMENTS PREVIOUSLY RECORDED PREVIOUSLY RECORDED ON REEL 017248 FRAME 0915;ASSIGNORS:HUFF, HANS-JOACHIM;SIENEL, TOBIAS H.;CHEN, YU;AND OTHERS;REEL/FRAME:017308/0719;SIGNING DATES FROM 20060201 TO 20060202 Owner name: CARRIER COMMERCIAL REFRIGERATION, INC., NORTH CARO Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE CORRECTIVE ASSIGNMENT TO RE-RECORD ASSIGNMENT TO CORRECT DOCKET NUMBER AND ATTACHMENTS PREVIOUSLY RECORDED PREVIOUSLY RECORDED ON REEL 017248 FRAME 0915. ASSIGNOR(S) HEREBY CONFIRMS THE CHANGE DOCKET NUMBER FROM 02-236WO TO 05-263WO;ASSIGNORS:HUFF, HANS-JOACHIM;SIENEL, TOBIAS H.;CHEN, YU;AND OTHERS;SIGNING DATES FROM 20060201 TO 20060202;REEL/FRAME:017308/0719 |
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