WO2006101569A2 - Accumulator integration with exchanger header - Google Patents

Accumulator integration with exchanger header Download PDF

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Publication number
WO2006101569A2
WO2006101569A2 PCT/US2005/047574 US2005047574W WO2006101569A2 WO 2006101569 A2 WO2006101569 A2 WO 2006101569A2 US 2005047574 W US2005047574 W US 2005047574W WO 2006101569 A2 WO2006101569 A2 WO 2006101569A2
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
accumulator
compressor
zone
Prior art date
Application number
PCT/US2005/047574
Other languages
French (fr)
Other versions
WO2006101569A3 (en
Inventor
Hans-Joachim Huff
Tobias Sienel
Yu Chen
Parmesh Verma
Original Assignee
Carrier Commericial Refrigeration, Inc.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Carrier Commericial Refrigeration, Inc. filed Critical Carrier Commericial Refrigeration, Inc.
Priority to EP05856047A priority Critical patent/EP1864059A2/en
Priority to JP2008501868A priority patent/JP2008533430A/en
Priority to US11/908,450 priority patent/US20080190122A1/en
Publication of WO2006101569A2 publication Critical patent/WO2006101569A2/en
Publication of WO2006101569A3 publication Critical patent/WO2006101569A3/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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

Abstract

A refrigeration system 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.

Description

ACCUMULATOR INTEGRATION WITH HEAT EXCHANGER HEADER
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] This application claims the benefit of the filing date of earlier filed Provisional Application Serial No. 60/663,911 filed March 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 Serial 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.
BACKGROUND OF THE INVENTION
[0002] 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. [0003] 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. In 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.
[0004] While the system illustrated in Fig. 1 is functional, as set forth above, a functional system which occupies less space is desirable.
[0005] It is therefore the primary object of the present invention to provide such a system. [0006] Other objects and advantages will appear herein. SUMMARY OF THE INVENTION
[0007] 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. [0008] 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.
BRIEF DESCRIPTION OF THE DRAWING
[0009] A detailed description of preferred embodiments of the present invention follows, with reference to the attached drawings, wherein: [0010] Fig. 1 is an illustration of a prior art vapor compression system; [0011] Fig. 2 is a schematic illustration of a system having a combined accumulator and header according to the invention;
[0012] Fig. 3 is a schematic illustration of an alternative embodiment of the combined accumulator and header according to the invention; and [0013] Fig. 4 is a schematic illustration of a further alternative embodiment of the combined accumulator and header in accordance with the present invention.
DETAILED DESCRIPTION [0014] 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).
[0015] 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. As compared to Fig. 1, it should be readily appreciated that 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.
[0016] As shown in Fig. 2, 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. Flow enters the combined header and accumulator 22 directly from tubes 28 of second heat exchanger 18. In this regard, it is noted that 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. As shown in Fig. 2, this chamber is defined by side, front, back, top and bottom walls around the end of the heat exchanger tubes.
[0017] Also as shown in Fig. 2, 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. [0018] 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.
[0019] 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. Specific examples of suitable heat exchangers include but are not limited to wire on tube heat exchangers, fin heat exchangers, and the like.
[0020] 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.
[0021] 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.
[0022] Header and accumulator 22 can advantageously be incorporated into heat exchanger 18 as shown in Fig. 2. Alternatively, 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. [0023] Fig. 3 shows a further alternative embodiment of the present invention, having the same basic components as the embodiment of Fig. 2. In the embodiment of Fig. 3, 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. In this embodiment, it should be noted that by positioning lower most tube 30 sufficiently high on second heat exchanger 18, the lower liquid refrigerant zone 24 can be defined within combined accumulator and header 22 so that a bottom surface 44 of combined accumulator and header 22 does not extend substantially beyond a bottom surface 46 of second heat exchanger 18. Conduit 42 is preferably very short, most preferably having a length of less than about 5 inches.
[0024] 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. With the embodiment of Fig. 4, 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.
[0025] 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. 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.
[0026] 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. [0027] 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

CLAIMS What is claimed is:
1. A refrigeration system comprising: 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.
2. The system of claim 1 wherein the combined header and accumulator comprises a chamber communicated with refrigerant flow paths of the second heat exchanger for receiving two phase refrigerant flow and defining therein a lower liquid refrigerant zone and an upper vapor refrigerant zone.
3. The system of claim 2, wherein the lower liquid refrigerant zone is defined below a lower most flow port between the second heat exchanger and the combined header and accumulator.
4. The system of claim 3, wherein the lower most flow port is positioned high enough above the lower liquid refrigerant zone that the lower liquid refrigerant zone does not extend beyond the evaporator.
5. The system of claim 1, wherein tubes of the second heat exchanger flow directly into the combined header and accumulator.
6. The system of claim 5, wherein a vapor flow line is connected directly from the combined header and accumulator to the compressor.
7. The system of claim 2 further comprising a conduit communicated with the upper vapor refrigerant zone for conveying vapor refrigerant to the compressor.
8. The system of claim 7, wherein the conduit extends upwardly through the liquid refrigerant zone into the vapor refrigerant zone, and is also communicated with the liquid refrigerant zone.
9. The system of claim 8, wherein the conduit is communicated with the liquid refrigerant zone through a pin-hole to allow oil to return to the compressor.
10. The system of claim 1 wherein: the refrigerant comprises, a transcritical vapor system refrigerant and wherein the first and second heat exchangers are refrigerant-air heat exchangers.
11. A-beverage cooling device comprising the system of claim 1.
12. A method for operating a refrigeration system comprising 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.
13. The method of claim 12, wherein the second heat exchanger comprises a flow tube, wherein operation of the compressor creates two-phase refrigerant in the flow tube, and wherein the two-phase refrigerant flows directly to the combined header and accumulator.
14. The method of claim 12, wherein the refrigerant is a transcritical vapor system refrigerant.
15. The method of claim 12, wherein the refrigerant is CO2.
16. The method of claim 12, wherein the combined header and accumulator defines a lower liquid refrigerant zone and an upper vapor refrigerant zone, and wherein flow of refrigerant into the combined header and accumulator causes separation of the refrigerant into a liquid refrigerant in the lower liquid refrigerant zone and vapor refrigerant in the upper vapor refrigerant zone.
PCT/US2005/047574 2005-03-18 2005-12-30 Accumulator integration with exchanger header WO2006101569A2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP05856047A EP1864059A2 (en) 2005-03-18 2005-12-30 Accumulator integration with exchanger header
JP2008501868A JP2008533430A (en) 2005-03-18 2005-12-30 Accumulator integrated with heat exchanger header
US11/908,450 US20080190122A1 (en) 2005-03-18 2005-12-30 Accumulator Integration with Heat Exchanger Header

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US66391105P 2005-03-18 2005-03-18
US60/663,911 2005-03-18

Publications (2)

Publication Number Publication Date
WO2006101569A2 true WO2006101569A2 (en) 2006-09-28
WO2006101569A3 WO2006101569A3 (en) 2007-12-06

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PCT/US2005/047574 WO2006101569A2 (en) 2005-03-18 2005-12-30 Accumulator integration with exchanger header

Country Status (5)

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US (1) US20080190122A1 (en)
EP (1) EP1864059A2 (en)
JP (1) JP2008533430A (en)
CN (1) CN101203720A (en)
WO (1) WO2006101569A2 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
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WO2008124637A2 (en) * 2007-04-05 2008-10-16 Johnson Controls Technology Company Heat exchanger
EP2450646A1 (en) * 2010-11-08 2012-05-09 Honeywell International, Inc. Integrated evaporator and accumulator for refrigerant systems
CN111316044A (en) * 2017-11-15 2020-06-19 三菱电机株式会社 Outdoor unit of air conditioner

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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
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
JP5772904B2 (en) * 2013-09-02 2015-09-02 ダイキン工業株式会社 Heat recovery type refrigeration system
US10323869B2 (en) * 2016-10-05 2019-06-18 Johnson Control Technology Company Combined suction header and accumulator unit
JP6805473B2 (en) * 2017-01-31 2020-12-23 荏原冷熱システム株式会社 Absorption chiller
IT201900003427A1 (en) * 2019-03-08 2020-09-08 Lu Ve Spa INTAKE MANIFOLD WITH UPWARD OUTLET FOR EVAPORATORS OF REFRIGERATION SYSTEMS.

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Cited By (8)

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WO2008124637A2 (en) * 2007-04-05 2008-10-16 Johnson Controls Technology Company Heat exchanger
WO2008124637A3 (en) * 2007-04-05 2008-12-18 Johnson Controls Tech Co Heat exchanger
CN101652611B (en) * 2007-04-05 2012-09-05 江森自控科技公司 System and method for performing refrigerant loop
US9410709B2 (en) 2007-04-05 2016-08-09 Johnson Controls Technology Company Multichannel condenser coil with refrigerant storage receiver
EP2450646A1 (en) * 2010-11-08 2012-05-09 Honeywell International, Inc. Integrated evaporator and accumulator for refrigerant systems
US9062900B2 (en) 2010-11-08 2015-06-23 Honeywell International Inc. Integrated evaporator and accumulator for refrigerant systems
CN111316044A (en) * 2017-11-15 2020-06-19 三菱电机株式会社 Outdoor unit of air conditioner
EP3712517A4 (en) * 2017-11-15 2020-09-23 Mitsubishi Electric Corporation Outdoor unit of air conditioner

Also Published As

Publication number Publication date
US20080190122A1 (en) 2008-08-14
JP2008533430A (en) 2008-08-21
EP1864059A2 (en) 2007-12-12
CN101203720A (en) 2008-06-18
WO2006101569A3 (en) 2007-12-06

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