EP1872068B1 - Multi-part heat exchanger - Google Patents

Multi-part heat exchanger Download PDF

Info

Publication number
EP1872068B1
EP1872068B1 EP05856004.6A EP05856004A EP1872068B1 EP 1872068 B1 EP1872068 B1 EP 1872068B1 EP 05856004 A EP05856004 A EP 05856004A EP 1872068 B1 EP1872068 B1 EP 1872068B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
component
heat
refrigerant
flow
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.)
Active
Application number
EP05856004.6A
Other languages
German (de)
French (fr)
Other versions
EP1872068A4 (en
EP1872068A2 (en
Inventor
Tobias Sienel
Yu Chen
Parmesh Verma
Hans-Joachim Huff
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Taylor Commercial FoodService LLC
Original Assignee
Carrier Comercial 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 Comercial Refrigeration Inc filed Critical Carrier Comercial Refrigeration Inc
Publication of EP1872068A2 publication Critical patent/EP1872068A2/en
Publication of EP1872068A4 publication Critical patent/EP1872068A4/en
Application granted granted Critical
Publication of EP1872068B1 publication Critical patent/EP1872068B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B6/00Compression machines, plants or systems, with several condenser circuits
    • F25B6/04Compression machines, plants or systems, with several condenser circuits arranged in series
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008Compression 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25DREFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • F25D19/02Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors plug-in type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00Gas cycle refrigeration machines
    • F25B2309/06Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25DREFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D23/00General constructional features
    • F25D23/003General constructional features for cooling refrigerating machinery
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25DREFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2317/00Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/06Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
    • F25D2317/065Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air return
    • F25D2317/0651Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air return through the bottom
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25DREFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2317/00Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/06Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
    • F25D2317/066Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air supply
    • F25D2317/0661Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air supply from the bottom
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25DREFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2323/00General constructional features not provided for in other groups of this subclass
    • F25D2323/002Details for cooling refrigerating machinery
    • F25D2323/0026Details for cooling refrigerating machinery characterised by the incoming air flow
    • F25D2323/00264Details for cooling refrigerating machinery characterised by the incoming air flow through the front bottom part
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25DREFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2323/00General constructional features not provided for in other groups of this subclass
    • F25D2323/002Details for cooling refrigerating machinery
    • F25D2323/0027Details for cooling refrigerating machinery characterised by the out-flowing air
    • F25D2323/00271Details for cooling refrigerating machinery characterised by the out-flowing air from the back bottom
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25DREFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2500/00Problems to be solved
    • F25D2500/02Geometry problems

Definitions

  • the invention relates to vapor compression systems and, more particularly, to a heat exchanger configuration for such a system.
  • An exemplary heat exchanger system according to the preamble of claim 1 is disclosed in JP 6-207773 .
  • the heat exchanger placement is very much constrained by space.
  • the efficiency of the system is often low in comparison to a system with a properly sized heat exchanger due to the large temperature difference between the air and the refrigerant in the heat exchangers.
  • the present invention provides 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 first heat exchanger comprises at least a first heat exchanger component and a second heat exchanger component arranged along a flow path of heat exchange fluid for the first heat exchanger, the first heat exchanger component being downstream of the second heat exchanger in the first mode; and wherein a fan is arranged to provide a flow of heat exchange medium past the first heat exchanger, such that the first heat exchanger component is upstream of the second heat exchanger component in the flow of heat exchange medium; characterised by a refrigerator housing defining a cassette receiving area, wherein the heat exchanger components are mounted within a cassette adapted to be inserted into
  • the invention relates to a vapor compression system of a refrigerator unit and, more particularly, to the arrangement of a heat exchanger in a vapor compression system, preferably in a transcritical vapor compression system.
  • greater contact area between the heat exchanger and heat exchange medium is obtained by utilizing all potentially available spaces within a particular vapor compression system to house additional components of a heat exchanger, such that the heat exchanger is implemented in a series or plurality of heat exchange components. In this manner, small available spaces are nevertheless utilized to increase heat exchange efficiency and, therefore, efficiency of the overall system.
  • FIG. 1 shows a system in accordance with the present invention.
  • system 10 which, in this particular embodiment, is the vapor compression system for a bottle cooler refrigeration assembly.
  • FIG. 1 shows the lower portion of such an assembly, including a housing 12 containing a vapor compression system.
  • FIGS.1 - 3 for further discussion of the vapor compression system, which includes a compressor 14, a downstream heat exchanger 16, an expansion device 18 and an evaporator 20.
  • Compressor 14 is operative to drive a refrigerant along refrigerant lines ( FIG.3 ) first to heat exchanger 16, then to expansion device 18, and then to evaporator 20. Refrigerant flows from evaporator 20 back to compressor 14 to complete the circuit.
  • first heat exchanger 16 is provided having a first heat exchange component 22 and a second heat exchange component 24. These components are positioned within housing 12 to take advantage of the spaces available such that high amounts of heat exchange can be accomplished with relatively small available spaces.
  • housing 12 defines a flow path for heat exchange medium, for example air, to enter into heat exchange relationship with first heat exchanger 16.
  • An upper portion of housing 12 also defines a flow path for air from within the refrigerated space (not shown, but located above housing 12 and supplied with air cooled by arrows 27) to be treated with second heat exchanger 20.
  • first and second components 22, 24 of first heat exchanger 16 can and most likely will be different in size and/or shape so that these components can advantageously take advantage of the available space within a particular device.
  • first component 22 has a relatively larger area in a transverse plane with respect to the flow, and is relatively thin from front to back. This is because first component 22 in this embodiment is sized to fit within a relatively narrow (from front to back) space toward the open front of housing 12.
  • a second space within housing 12 in this embodiment is available beneath a wall 28 which separates one portion of housing 12 for treating the first flow of air 26 from a second portion of housing 12 for treating the second portion of air 27.
  • This wall 28 extends downwardly relative to the outer contour of housing 12, and results in a restriction in flow area as air flows from the inlet end 30 to the outlet end 32 of housing 12.
  • This zone of decreased cross sectional flow area results in an increase in velocity of the air flowing through this zone.
  • An increased velocity flow has been found to provide improved efficiency heat exchange in heat exchangers such as that of the present invention.
  • this zone has a substantially short height and yet extends much further from the inlet side toward the outlet side as compared to the space for accommodating first component 22.
  • second component 24 is advantageously shaped and adapted to fit properly within this space, thereby providing maximum possible heat exchange area and further taking advantage of the increased flow velocity of air through that zone.
  • one preferred implementation of the vapor compression system in accordance with the present invention is a transcritical vapor compression system.
  • a transcritical vapor compression system operates upon a refrigerant which does not condense in the first heat exchanger.
  • a refrigerant of a transcritical vapor compression system is CO 2 .
  • other refrigerants could be used well within the scope of the present invention to provide suitable vapor compression systems which would benefit from the heat exchanger arrangement of the present invention.
  • Expansion device 18 can be any suitable expansion device for decreasing the pressure of refrigerant passing there through as is known to a person of skill in the art. Various known expansion devices could be utilized for this purpose.
  • a pressure regulator such as that disclosed in WO 2006/101566 , is a particularly desirable type of expansion device for use in connection with the present invention. As used herein, the term expansion device is considered to include such a pressure regulator.
  • Second heat exchanger 20 which performs the function of an evaporator, is shown as a single heat exchanger in the drawings. It should be appreciated that second heat exchanger 20 could also be provided in a plurality of components, as well, in the event that space for treatment of flow of air from the refrigerated space is particularly small and/or irregularly shaped.
  • FIG. 3 shows refrigerant lines connecting from first heat exchanger 16 to expansion device 18 and then to second heat exchanger or evaporator 20. Refrigerant flows from evaporator 20 back to the suction inlet of compressor 14.
  • the present invention provides for increased heat exchange efficiency due to increase in area of contact between the heat exchanger and the heat exchange medium. It should further be appreciated that the system of the present invention provides for enhanced utilization of space available for heat exchange, thereby providing more efficient operation of a vapor compression system as desired in accordance with the present invention.
  • FIG. 2 shows an example with a two part heat exchanger.
  • the refrigerant flow would be circuited first through component 24 and then through component 22 if the air flow was directed from front to back.
  • the refrigerant flow would be circuited first through component 22 and then through component 24 if the air flow was from back to front.
  • This concept is especially useful for transcritical vapor compression systems (such as using CO 2 ), where it is critically important for efficiency that the temperature of refrigerant leaving the heat rejecting heat exchanger be as close as possible to the heat sink fluid (typically air) entering the heat exchanger.
  • the individual heat exchanger segments or components could also be circuited to be as counterflow as possible to further enhance this effect.
  • the segments or components of the heat exchanger could be manufactured and shipped as one piece, or separately manufactured and connected during the unit assembly process.
  • This type of a heat exchanger is particularly useful for applications where a low number of fins are used on the heat exchanger for reasons of fouling.
  • the reduction in fins due to fouling concerns is offset by the additional heat exchanger tube or channel surface area.
  • This heat exchanger could be a round tube plate fin, wire on tube, microchannel, or any other configuration.

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)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)

Description

    BACKGROUND OF THE INVENTION
  • The invention relates to vapor compression systems and, more particularly, to a heat exchanger configuration for such a system. An exemplary heat exchanger system according to the preamble of claim 1 is disclosed in JP 6-207773 .
  • In many vapor compression systems, the heat exchanger placement is very much constrained by space. For these applications, the efficiency of the system is often low in comparison to a system with a properly sized heat exchanger due to the large temperature difference between the air and the refrigerant in the heat exchangers.
  • The need exists for more efficient heat exchange despite space requirements of the system, and it is an object of the invention to provide such a system.
  • Other objects and advantages will appear herein below.
  • SUMMARY OF THE INVENTION
  • According to the present invention, the foregoing objects and advantages have been attained.
  • The present invention provides 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 first heat exchanger comprises at least a first heat exchanger component and a second heat exchanger component arranged along a flow path of heat exchange fluid for the first heat exchanger, the first heat exchanger component being downstream of the second heat exchanger in the first mode; and wherein a fan is arranged to provide a flow of heat exchange medium past the first heat exchanger, such that the first heat exchanger component is upstream of the second heat exchanger component in the flow of heat exchange medium; characterised by a refrigerator housing defining a cassette receiving area, wherein the heat exchanger components are mounted within a cassette adapted to be inserted into the receiving area, and wherein the second heat exchanger component is in a zone of decreased cross-sectional flow area in the flow of heat exchange medium, whereby the velocity is increased.
  • BRIEF DESCRIPTION OF THE DRAWINGS
  • A detailed description of preferred embodiments of the invention follows with reference to the attached drawings, wherein:
    • FIG. 1 is a perspective view of a system having a multi-part heat exchanger according to the invention;
    • FIG. 2 is a schematic illustration of a multi-part heat exchanger system according to the invention: and
    • FIG. 3 illustrates the refrigerant and air flow in a system according to the invention.
    DETAILED DESCRIPTION
  • The invention relates to a vapor compression system of a refrigerator unit and, more particularly, to the arrangement of a heat exchanger in a vapor compression system, preferably in a transcritical vapor compression system.
  • As set forth above, the greater the area of heat exchanger contact with heat exchange medium such as air, the greater the efficiency in operation of a vapor compression system. In accordance with the present invention, greater contact area between the heat exchanger and heat exchange medium is obtained by utilizing all potentially available spaces within a particular vapor compression system to house additional components of a heat exchanger, such that the heat exchanger is implemented in a series or plurality of heat exchange components. In this manner, small available spaces are nevertheless utilized to increase heat exchange efficiency and, therefore, efficiency of the overall system.
  • FIG. 1 shows a system in accordance with the present invention. FIG. 1 shows system 10 which, in this particular embodiment, is the vapor compression system for a bottle cooler refrigeration assembly. FIG. 1 shows the lower portion of such an assembly, including a housing 12 containing a vapor compression system. Reference is made to FIGS.1 - 3 for further discussion of the vapor compression system, which includes a compressor 14, a downstream heat exchanger 16, an expansion device 18 and an evaporator 20. Compressor 14 is operative to drive a refrigerant along refrigerant lines (FIG.3) first to heat exchanger 16, then to expansion device 18, and then to evaporator 20. Refrigerant flows from evaporator 20 back to compressor 14 to complete the circuit.
  • In accordance with the present invention, first heat exchanger 16 is provided having a first heat exchange component 22 and a second heat exchange component 24. These components are positioned within housing 12 to take advantage of the spaces available such that high amounts of heat exchange can be accomplished with relatively small available spaces.
  • As illustrated in the drawings, housing 12 defines a flow path for heat exchange medium, for example air, to enter into heat exchange relationship with first heat exchanger 16. An upper portion of housing 12 also defines a flow path for air from within the refrigerated space (not shown, but located above housing 12 and supplied with air cooled by arrows 27) to be treated with second heat exchanger 20.
  • In connection with any heat exchange system, and particularly in connection with vapor compression systems which form the preferred embodiment of the present invention, extended area of heat exchange contact between the heat exchange medium and the refrigerant-carrying heat exchangers is critical to obtaining good efficiency of the system. It has also been found that such systems operate most efficiently with counter-current flow of refrigerant verses heat exchange medium. That is, referring to FIG. 3, if heat exchange medium or air is flowing in the direction of arrows 26, it is preferred that refrigerant flow through heat exchanger 16 be in the flow direction shown such that the direction of flow of refrigerant is counter to that of the flow of heat exchange medium. Referring further to FIGS. 1 - 3, it should readily apparent that first and second components 22, 24 of first heat exchanger 16 can and most likely will be different in size and/or shape so that these components can advantageously take advantage of the available space within a particular device. For example, in the embodiment shown, first component 22 has a relatively larger area in a transverse plane with respect to the flow, and is relatively thin from front to back. This is because first component 22 in this embodiment is sized to fit within a relatively narrow (from front to back) space toward the open front of housing 12. A second space within housing 12 in this embodiment is available beneath a wall 28 which separates one portion of housing 12 for treating the first flow of air 26 from a second portion of housing 12 for treating the second portion of air 27. This wall 28 extends downwardly relative to the outer contour of housing 12, and results in a restriction in flow area as air flows from the inlet end 30 to the outlet end 32 of housing 12. This zone of decreased cross sectional flow area results in an increase in velocity of the air flowing through this zone. An increased velocity flow has been found to provide improved efficiency heat exchange in heat exchangers such as that of the present invention. According to the invention, it is preferred to position second component 24 of first heat exchanger 16 within this zone of decreased cross sectional flow area so as to take advantage of the increased flow of velocity in this zone: Further, the shape of this zone dictates a different configuration for second component 24 as compared to first component 22. Specifically, this zone has a substantially short height and yet extends much further from the inlet side toward the outlet side as compared to the space for accommodating first component 22. Thus, second component 24 is advantageously shaped and adapted to fit properly within this space, thereby providing maximum possible heat exchange area and further taking advantage of the increased flow velocity of air through that zone.
  • As set forth above, one preferred implementation of the vapor compression system in accordance with the present invention is a transcritical vapor compression system. Such a system, as is known to a person of skill in the art, operates upon a refrigerant which does not condense in the first heat exchanger. One example of a refrigerant of a transcritical vapor compression system is CO2. Of course, other refrigerants could be used well within the scope of the present invention to provide suitable vapor compression systems which would benefit from the heat exchanger arrangement of the present invention.
  • Expansion device 18 can be any suitable expansion device for decreasing the pressure of refrigerant passing there through as is known to a person of skill in the art. Various known expansion devices could be utilized for this purpose. In accordance with a preferred aspect of the present invention, a pressure regulator, such as that disclosed in WO 2006/101566 , is a particularly desirable type of expansion device for use in connection with the present invention. As used herein, the term expansion device is considered to include such a pressure regulator.
  • Second heat exchanger 20, which performs the function of an evaporator, is shown as a single heat exchanger in the drawings. It should be appreciated that second heat exchanger 20 could also be provided in a plurality of components, as well, in the event that space for treatment of flow of air from the refrigerated space is particularly small and/or irregularly shaped.
  • FIG. 3 shows refrigerant lines connecting from first heat exchanger 16 to expansion device 18 and then to second heat exchanger or evaporator 20. Refrigerant flows from evaporator 20 back to the suction inlet of compressor 14.
  • It should be appreciated that the present invention provides for increased heat exchange efficiency due to increase in area of contact between the heat exchanger and the heat exchange medium. It should further be appreciated that the system of the present invention provides for enhanced utilization of space available for heat exchange, thereby providing more efficient operation of a vapor compression system as desired in accordance with the present invention.
  • In some systems it is possible to use a heat exchanger divided into multiple parts and arranged where space is available to increase the overall heat transfer area of the heat exchanger. This disclosure makes use of this with the addition of arranging the multiple parts of the heat exchanger in such a way that the effective refrigerant flows and air (or other heat transfer mediums) flows are opposite to each other.
  • FIG. 2 shows an example with a two part heat exchanger. In this case the refrigerant flow would be circuited first through component 24 and then through component 22 if the air flow was directed from front to back. The refrigerant flow would be circuited first through component 22 and then through component 24 if the air flow was from back to front. This concept is especially useful for transcritical vapor compression systems (such as using CO2), where it is critically important for efficiency that the temperature of refrigerant leaving the heat rejecting heat exchanger be as close as possible to the heat sink fluid (typically air) entering the heat exchanger. The individual heat exchanger segments or components could also be circuited to be as counterflow as possible to further enhance this effect.
  • In FIG. 2, only one fan 34 is used to move the heat transfer fluid (air) through all of the heat exchanger components 22, 24. This is an additional benefit to cost and energy efficiency, although this is not a necessary embodiment.
  • The segments or components of the heat exchanger could be manufactured and shipped as one piece, or separately manufactured and connected during the unit assembly process. This type of a heat exchanger is particularly useful for applications where a low number of fins are used on the heat exchanger for reasons of fouling. The reduction in fins due to fouling concerns is offset by the additional heat exchanger tube or channel surface area. This heat exchanger could be a round tube plate fin, wire on tube, microchannel, or any other configuration.
  • 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 scope of the invention as claimed. 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 (7)

  1. A refrigeration system (10) comprising:
    a compressor (14) for driving a refrigerant along a flow path in at least a first mode of system operation;
    a first heat exchanger (16) along the flow path downstream of the compressor in the first mode;
    a second heat exchanger (20) along the flow path upstream of the compressor in the first mode; and
    an expansion device (18) in the flow path downstream of the first heat exchanger and upstream of the second heat exchanger in the first mode,
    wherein the first heat exchanger comprises at least a first heat exchanger component (22) and a second heat exchanger component (24) arranged along a flow path of heat exchange fluid for the first heat exchanger, the first heat exchanger component (22) being downstream of the second heat exchanger component (24) in the first mode; and
    wherein a fan (34) is arranged to provide a flow of heat exchange medium past the first heat exchanger, such that the first heat exchanger component is upstream of the second heat exchanger component in the flow of heat exchange medium;
    characterised by a refrigerator housing defining a cassette receiving area, wherein the heat exchanger components (22, 24) are mounted within a cassette adapted to be inserted into the receiving area, and wherein the second heat exchanger component (24) is in a zone of decreased cross-sectional flow area in the flow of heat exchange medium, whereby the velocity is increased.
  2. The system of claim 1 wherein the second heat exchanger (20) also comprises a plurality of heat exchange components.
  3. The system of claim 1 wherein the first heat exchanger (16) is mounted within a housing having separate and discrete available spaces, and wherein the heat exchanger components (22, 24) are positioned in the spaces.
  4. The system of claim 1, wherein the first component (22) has a different shape than the second component (24).
  5. The system of claim 1, wherein the refrigerant comprises, in major mass part, CO2; and the first and second heat exchangers (16, 20) are refrigerant-air heat exchangers.
  6. The system of claim 1, wherein the system contains a refrigerant and the refrigerant is a transcritical vapor compression.
  7. A beverage cooling device comprising the system of claim 1.
EP05856004.6A 2005-03-18 2005-12-30 Multi-part heat exchanger Active EP1872068B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US66391705P 2005-03-18 2005-03-18
PCT/US2005/047524 WO2006101563A2 (en) 2005-03-18 2005-12-30 Multi-part heat exchanger

Publications (3)

Publication Number Publication Date
EP1872068A2 EP1872068A2 (en) 2008-01-02
EP1872068A4 EP1872068A4 (en) 2011-11-16
EP1872068B1 true EP1872068B1 (en) 2016-06-22

Family

ID=37024267

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05856004.6A Active EP1872068B1 (en) 2005-03-18 2005-12-30 Multi-part heat exchanger

Country Status (7)

Country Link
US (1) US20080184731A1 (en)
EP (1) EP1872068B1 (en)
JP (1) JP4705157B2 (en)
CN (1) CN100575813C (en)
ES (1) ES2580080T3 (en)
HK (1) HK1120103A1 (en)
WO (1) WO2006101563A2 (en)

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2936806B1 (en) 2008-10-08 2012-08-31 Arkema France REFRIGERANT FLUID
FR2950065B1 (en) 2009-09-11 2012-02-03 Arkema France BINARY REFRIGERANT FLUID
FR2950071B1 (en) 2009-09-11 2012-02-03 Arkema France TERNARY COMPOSITIONS FOR LOW CAPACITY REFRIGERATION
FR2950067B1 (en) * 2009-09-11 2011-10-28 Arkema France HEAT TRANSFER FLUID IN REPLACEMENT OF R-410A
FR2950070B1 (en) 2009-09-11 2011-10-28 Arkema France TERNARY COMPOSITIONS FOR HIGH CAPACITY REFRIGERATION
US10035938B2 (en) 2009-09-11 2018-07-31 Arkema France Heat transfer fluid replacing R-134a
FR2950066B1 (en) 2009-09-11 2011-10-28 Arkema France LOW AND MEDIUM TEMPERATURE REFRIGERATION
FR2950069B1 (en) 2009-09-11 2011-11-25 Arkema France USE OF TERNARY COMPOSITIONS
FR2950068B1 (en) * 2009-09-11 2012-05-18 Arkema France HEAT TRANSFER METHOD
FR2957083B1 (en) 2010-03-02 2015-12-11 Arkema France HEAT TRANSFER FLUID FOR CENTRIFUGAL COMPRESSOR
JP5127858B2 (en) * 2010-03-18 2013-01-23 三菱電機株式会社 Air conditioner for vehicles
FR2959999B1 (en) * 2010-05-11 2012-07-20 Arkema France HEAT TRANSFER FLUIDS AND THEIR USE IN COUNTER-CURRENT HEAT EXCHANGERS
FR2959997B1 (en) 2010-05-11 2012-06-08 Arkema France HEAT TRANSFER FLUIDS AND THEIR USE IN COUNTER-CURRENT HEAT EXCHANGERS
FR2964977B1 (en) 2010-09-20 2013-11-01 Arkema France COMPOSITION BASED ON 3,3,3-TETRAFLUOROPROPENE
US10184688B2 (en) 2011-12-28 2019-01-22 Desert Aire Corp. Air conditioning apparatus for efficient supply air temperature control
CA2879706C (en) * 2014-01-22 2016-11-08 Craig Michael Burg Heat pump non-reversing valve arrangement
US11506425B2 (en) 2017-12-18 2022-11-22 Daikin Industries, Ltd. Refrigeration cycle apparatus
US11441802B2 (en) 2017-12-18 2022-09-13 Daikin Industries, Ltd. Air conditioning apparatus
US11820933B2 (en) * 2017-12-18 2023-11-21 Daikin Industries, Ltd. Refrigeration cycle apparatus
US11906207B2 (en) 2017-12-18 2024-02-20 Daikin Industries, Ltd. Refrigeration apparatus
BR112020010634A2 (en) 2017-12-18 2020-11-10 Daikin Industries, Ltd. composition comprising refrigerant, use of the same, refrigeration machine having the same, and method for operating said refrigeration machine
US11493244B2 (en) 2017-12-18 2022-11-08 Daikin Industries, Ltd. Air-conditioning unit
US11365335B2 (en) 2017-12-18 2022-06-21 Daikin Industries, Ltd. Composition comprising refrigerant, use thereof, refrigerating machine having same, and method for operating said refrigerating machine
US11441819B2 (en) 2017-12-18 2022-09-13 Daikin Industries, Ltd. Refrigeration cycle apparatus
KR102655619B1 (en) 2017-12-18 2024-04-09 다이킨 고교 가부시키가이샤 refrigeration cycle device
US11549041B2 (en) 2017-12-18 2023-01-10 Daikin Industries, Ltd. Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator
US11435118B2 (en) 2017-12-18 2022-09-06 Daikin Industries, Ltd. Heat source unit and refrigeration cycle apparatus
US11549695B2 (en) 2017-12-18 2023-01-10 Daikin Industries, Ltd. Heat exchange unit

Family Cites Families (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2278226A (en) * 1941-03-03 1942-03-31 Halsey W Taylor Fluid cooler
US2401560A (en) * 1944-01-31 1946-06-04 Gen Motors Corp Refrigerating apparatus
US2723540A (en) * 1953-04-02 1955-11-15 Int Harvester Co Air conditioner condenser incorporating condensate disposal means thereon
US2941382A (en) * 1959-01-20 1960-06-21 Westinghouse Electric Corp Condensate disposal means for selfcontained air conditioners
US4207748A (en) * 1967-06-22 1980-06-17 Nebgen William H Heat exchange device and method
JPS61225565A (en) * 1985-03-29 1986-10-07 松下精工株式会社 Outdoor machine for separation type air conditioner
US5157941A (en) * 1991-03-14 1992-10-27 Whirlpool Corporation Evaporator for home refrigerator
US5347827A (en) * 1992-07-01 1994-09-20 The Coca-Cola Company Modular refrigeration apparatus
JPH0634257A (en) * 1992-07-15 1994-02-08 Toshiba Corp Heat exchanger
JPH06207773A (en) 1993-01-11 1994-07-26 Toshiba Corp Refrigerator
US5664436A (en) * 1996-04-29 1997-09-09 Lancer Corporation Component configuration for enhancing dispenser serviceability
JP3540530B2 (en) * 1996-12-13 2004-07-07 東芝キヤリア株式会社 Air conditioner
US6467279B1 (en) * 1999-05-21 2002-10-22 Thomas J. Backman Liquid secondary cooling system
US6378324B1 (en) * 1999-10-26 2002-04-30 Crane Co. Thermally regulated storage container
DE19957719A1 (en) * 1999-11-30 2001-05-31 Bsh Bosch Siemens Hausgeraete Refrigerator has coolant feed stage approximately completely filled with liquid coolant as regards coolant accommodation volume during compressor idle periods
AUPR428001A0 (en) * 2001-04-06 2001-05-17 OYL Research and Development Centre SDN.BHD. (a company incorporated under the laws of Malaysia) Room air-conditioner
US6928833B2 (en) * 2001-10-22 2005-08-16 Showa Denko K.K. Finned tube for heat exchangers, heat exchanger, process for producing heat exchanger finned tube, and process for fabricating heat exchanger
JP2003287342A (en) * 2002-03-28 2003-10-10 Toshiba Corp Refrigerator
US6550270B2 (en) * 2002-05-24 2003-04-22 The Coca-Cola Company Seal compression mechanism for a refrigeration device
JP2004218925A (en) * 2003-01-15 2004-08-05 Fujitsu General Ltd Air conditioner
TWI267611B (en) * 2003-09-16 2006-12-01 Lg Electronics Inc Integral type air conditioner and air guide structure thereof
US7117689B2 (en) * 2004-02-02 2006-10-10 The Coca-Cola Company Removable refrigeration cassette for a hot and cold vending machine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
JP4705157B2 (en) 2011-06-22
EP1872068A4 (en) 2011-11-16
WO2006101563A2 (en) 2006-09-28
CN100575813C (en) 2009-12-30
US20080184731A1 (en) 2008-08-07
JP2008533425A (en) 2008-08-21
CN101175952A (en) 2008-05-07
HK1120103A1 (en) 2009-03-20
WO2006101563A3 (en) 2008-01-17
EP1872068A2 (en) 2008-01-02
ES2580080T3 (en) 2016-08-19

Similar Documents

Publication Publication Date Title
EP1872068B1 (en) Multi-part heat exchanger
EP1808654B1 (en) Vapor compression refrigerating systems and modules which comprise a heat exchanger disposed within a gas-liquid separator
US20120222846A1 (en) Unitary heat pump air conditioner having a heat exchanger with an integral receiver and sub-cooler
KR101120223B1 (en) Refrigeration cycle device
EP2629040B1 (en) A unitary heat pump air conditioner having a heat exchanger with an integral receiver and sub-cooler.
US6793010B1 (en) Heat exchanger having non-perpendicularly aligned heat transfer elements
US10612823B2 (en) Condenser
EP2971982B1 (en) Modular coil for air cooled chillers
EP3073218A1 (en) Water cooled microchannel condenser
US20080184713A1 (en) Heat Exchanger Arrangement
JP6458680B2 (en) Heat exchanger
US20080190122A1 (en) Accumulator Integration with Heat Exchanger Header
JP5316465B2 (en) Evaporator unit
US7475565B2 (en) Refrigeration system including a side-load sub-cooler
CN104515328A (en) Condenser for compression refrigerating machine
EP2570751B1 (en) Cooling system
US20170261270A1 (en) Compact tube and plate condenser with cooling fins
KR100493697B1 (en) The refrigerator for improvement on heat exchange efficiency
CN107421168A (en) Condenser
KR20050002652A (en) The refrigerator for improvement on heat exchange efficiency
US9903663B2 (en) Brazed heat exchanger with fluid flow to serially exchange heat with different refrigerant circuits
CN109312986B (en) Refrigeration device having a refrigerant liquefier with a sheet assembly
US20080149310A1 (en) Accelerated heat exchanger
CN117795662A (en) Power electronics cooling loop for refrigerant compressor
US20170108289A1 (en) Heat exchanger and a method for forming a heat exchanger

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: 20071018

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

R17D Deferred search report published (corrected)

Effective date: 20080117

RIN1 Information on inventor provided before grant (corrected)

Inventor name: HUFF, HANS-JOACHIM

Inventor name: VERMA, PARMESH

Inventor name: CHEN, YU

Inventor name: SIENEL, TOBIAS

RIN1 Information on inventor provided before grant (corrected)

Inventor name: CHEN, YU

Inventor name: VERMA, PARMESH

Inventor name: SIENEL, TOBIAS

Inventor name: HUFF, HANS-JOACHIM

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20111019

RIC1 Information provided on ipc code assigned before grant

Ipc: F25D 23/00 20060101ALN20111013BHEP

Ipc: F25B 1/00 20060101AFI20111013BHEP

17Q First examination report despatched

Effective date: 20141009

REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 602005049587

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F25B0001000000

Ipc: F25B0006040000

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 6/04 20060101AFI20151105BHEP

Ipc: F25D 19/02 20060101ALI20151105BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20151211

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAR Information related to intention to grant a patent recorded

Free format text: ORIGINAL CODE: EPIDOSNIGR71

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

INTG Intention to grant announced

Effective date: 20160517

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 807904

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160715

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602005049587

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2580080

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20160819

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 807904

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160622

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160923

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161022

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161024

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602005049587

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20170323

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 602005049587

Country of ref document: DE

Representative=s name: SCHMITT-NILSON SCHRAUD WAIBEL WOHLFROM PATENTA, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 602005049587

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20161230

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161231

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161231

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161230

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161230

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161230

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20051230

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160622

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20181123

Year of fee payment: 14

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 602005049587

Country of ref document: DE

Owner name: CARRIER CORPORATION, PALM BEACH GARDENS, US

Free format text: FORMER OWNER: CARRIER COMMERCIAL REFRIGERATION, INC., CHARLOTTE, N.C., US

Ref country code: DE

Ref legal event code: R082

Ref document number: 602005049587

Country of ref document: DE

REG Reference to a national code

Ref country code: ES

Ref legal event code: PC2A

Owner name: CARRIER CORPORATION

Effective date: 20190306

REG Reference to a national code

Ref country code: NL

Ref legal event code: HC

Owner name: TAYLOR COMMERCIAL FOODSERVICE INC.; US

Free format text: DETAILS ASSIGNMENT: CHANGE OF OWNER(S), CHANGE OF OWNER(S) NAME; FORMER OWNER NAME: CARRIER COMMERCIAL REFRIGERATION, INC.

Effective date: 20190225

Ref country code: NL

Ref legal event code: PD

Owner name: CARRIER CORPORATION; US

Free format text: DETAILS ASSIGNMENT: CHANGE OF OWNER(S), ASSIGNMENT; FORMER OWNER NAME: TAYLOR COMMERCIAL FOODSERVICE INC.

Effective date: 20190225

REG Reference to a national code

Ref country code: NL

Ref legal event code: MM

Effective date: 20200101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200101

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20221122

Year of fee payment: 18

Ref country code: DE

Payment date: 20221122

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20230102

Year of fee payment: 18