EP3783281A1 - Refrigeration system - Google Patents

Refrigeration system Download PDF

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Publication number
EP3783281A1
EP3783281A1 EP19192999.1A EP19192999A EP3783281A1 EP 3783281 A1 EP3783281 A1 EP 3783281A1 EP 19192999 A EP19192999 A EP 19192999A EP 3783281 A1 EP3783281 A1 EP 3783281A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
refrigeration system
inlet
separator
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP19192999.1A
Other languages
German (de)
French (fr)
Inventor
Thomas Lund
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.)
Danfoss AS
Original Assignee
Danfoss AS
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 Danfoss AS filed Critical Danfoss AS
Priority to EP19192999.1A priority Critical patent/EP3783281A1/en
Priority to CN202080059151.8A priority patent/CN114270117A/en
Priority to US17/635,404 priority patent/US20220275986A1/en
Priority to PCT/EP2020/073269 priority patent/WO2021032810A1/en
Publication of EP3783281A1 publication Critical patent/EP3783281A1/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

Definitions

  • the present invention relates to a refrigeration system comprising a refrigerant circuit having a first heat exchanger, a compressor, a second heat exchanger, and a separator connected to an outlet of the first heat exchanger.
  • a refrigerant is circulated. Gaseous refrigerant is compressed by the compressor. This leads to an increased temperature.
  • the so-called condenser When the compressed refrigerant gas is guided through a heat exchanger, the so-called condenser, it is cooled and changes from the gaseous state to a liquid state.
  • the liquid refrigerant is then supplied to the other heat exchanger, the so-called evaporator.
  • the refrigerant is evaporated while drawing heat from the ambient air or any other fluid, so that the ambient air is cooled.
  • the refrigerant leaving the evaporator returns to the suction side of the compressor.
  • the refrigerant leaving the evaporator or first heat exchanger is in many cases not fully gaseous. It contains as well refrigerant in liquid form.
  • the liquid phase of the refrigerant may be up to 30 % of the whole refrigerant leaving the evaporator. This liquid refrigerant must be removed from the refrigerant flow in order to avoid a situation in which liquid enters the compressor. Liquid entering the compressor can damage or destroy the compressor. To this end, the separator is used.
  • the space available for the separator is limited.
  • the size of the separator is limited as well. This makes it difficult to reliably remove all liquid from the refrigerant flow.
  • the object underlying the invention is to remove liquid from the refrigerant flow even with limited size of the separator.
  • the separator comprises at least two flow paths arranged in parallel between an inlet and an outlet.
  • Such a design has more than one flow path in the separation zone.
  • the use of two or more flow paths arranged in parallel has the effect that the velocity of the refrigerant flow is decreased so that the liquid has more time to "fall" out of the refrigerant flow.
  • the length of the flow path can be reduced correspondingly.
  • the diameter of this section can be reduced and correspondingly the height of the separator can be kept small while maintaining the same area of the flow paths.
  • the flow paths are inclined in the same direction from the inlet to the outlet.
  • the outlet is arranged in a position higher than the position of the inlet in the direction of gravity.
  • the flow paths have the same angle of inclination.
  • Such an angle can be rather small, for example 5° or 10°. Liquid removed from the refrigerant flow has the same conditions in all flow paths to flow back to the input.
  • the flow paths have the same lengths. This is a simple design to make the flow resistance in all flow paths equal or almost equal.
  • the separator is symmetrical with respect to a line connecting the inlet and the outlet.
  • the flow through the flow paths can be made the same through all flow paths.
  • each flow path comprises at least one curvature.
  • a curvature provides a benficial flow path for the separation. The creation of turbulence is avoided or at least reduced helping the separation of the gaseous and the liquid refrigerant.
  • the number of flow paths is two. Although this is a rather small number, the area available for the flow is sufficient to pass the refrigerant flow with a velocity which is low enough to give the refrigerant liquid enough time to fall out of the flow.
  • the flow paths are arranged in tubes, wherein the tubes surround a tube free space.
  • the tubes form a kind of "donut", which is a simple constructional solution.
  • the tubes are arranged in form of a rectangle, wherein the inlet and the outlet are arranged at opposite sides of the rectangle.
  • the rectangle will have rounded or squared corners.
  • Such a rectangle form of the separator can easily be made by using generally available semi-finished products.
  • the first heat exchanger comprises a refrigerant inlet connected to a connecting pipe and a refrigerant outlet connected to the connecting pipe, wherein the inlet of the separator is connected to the connecting pipe.
  • Refrigerant in liquid form can be supplied to the connecting pipe up to a certain level. This has the effect that the same level of liquid refrigerant is available within the first heat exchanger.
  • This refrigerant is at least partly evaporated in the first heat exchanger and escapes at the refrigerant outlet. From there, the refrigerant flow consisting of a gaseous phase and of a liquid phase enters the separator. Liquid refrigerant removed from the refrigerant flow in the separator can flow back to the connecting pipe.
  • the connecting pipe is arranged in parallel to the direction of gravity.
  • the connecting pipe is arranged vertically. Liquid refrigerant removed from the refrigerant flow can directly flow down to the refrigerant inlet of the first heat exchanger.
  • coalescing means are arranged in a region at the inlet.
  • the coalescing means have the effect that liquid droplets contained in the refrigerant flow combine into larger drops or droplets so that it is easier to remove these droplets.
  • the coalescing means comprise a mesh, preferablymade of metal. Other materials are possible. This is a simple design of coalescing means.
  • impingement means are arranged in a region at the inlet.
  • Impingement means can be formed by a surface which is arranged perpendicular or almost perpendicular to a flow direction of the refrigerant flow. Thus, drops of liquid refrigerant hit the surface and can be removed from the surface by gravity.
  • Fig. 1 schematically shows a refrigeration system 1 comprising a refrigerant circuit having a first heat exchanger 2, a compressor 3, a second heat exchanger 4 and a separator 5.
  • the refrigerant circuit comprises an accumulator 6.
  • the first heat exchanger 2 is a plate heat exchanger. However, other types of heat exchangers can be used.
  • the first heat exchanger comprises a refrigerant inlet 7 and a refrigerant outlet 8.
  • a connecting pipe 9 is connected to the refrigerant inlet 7 and to the refrigerant outlet 8.
  • the connecting pipe 9 comprises an oil drain 10.
  • the connecting pipe 9 comprises an expansion valve 11 through which refrigerant in liquid form from the accumulator 6 can be supplied into the connecting pipe 9.
  • the expansion valve can be of a float type or another type, controlled by a liquid level measurement.
  • the connecting pipe 9 is oriented in vertical direction (corresponding to the direction of gravity).
  • the liquid level in the connecting pipe 9 is controlled to provide a driving force to move refrigerant through the heat exchanger.
  • the liquid refrigerant in the first heat exchanger 2 evaporates.
  • the evaporation needs substance to be cooled, which could be heat which is withdrawn from another fluid circulating through a secondary side of the first heat exchanger 2, a product contained in the first heat exchanger 2 or from ambient air around the first heat exchanger 2.
  • the column of liquid refrigerant within the connecting pipe 9 drives the refrigerant out of the refrigerant outlet 8 to an upper part of the column 9.
  • this refrigerant flow is not in all cases totally gaseous. In most cases it comprises a gaseous phase and a liquid phase. However, the liquid phase must not arrive at the compressor 3, since the compressor 3 can be damaged or destroyed, when liquid enters the compressor 3.
  • the compressor 3 compresses the gaseous refrigerant. This compression leads to an elevated temperature and pressure of the gaseous refrigerant.
  • the gaseous refrigerant with elevated temperature is guided through the second heat exchanger 4, wherein the heat of the gaseous refrigerant is transferred to a secondary fluid, such as the ambient air, water or glykol.
  • the temperature of the refrigerant is lowered and the refrigerant is liquified and guided to the accumulator 6.
  • the separator 5 is used.
  • the separator 5 comprises an inlet 12 connected to the connecting tube 9 and an outlet 13 connected to the compressor 3.
  • the separator 5 is in form of a donut, i.e. it forms a rectangle having rounded corners. More precisely, the separator provides two flow paths 14, 15. The flow path 14 is arranged within a tube 16 and the flow path 15 is arranged within a tube 17. Both tubes 16, 17 are connected in the region of the inlet 12 and in the region of the outlet 13. Both tubes 16, 17 have the same length and are inclined upwardly from the inlet 12 towards the outlet 13. The angle of inclination for both tubes 16, 17 is the same. This angle is in a region from 1° to 20°.
  • the separator 5 is symmetrical with respect to a line 18 connecting the inlet 12 and the outlet 13. This means that both flow paths 14, 15 have the same flow resistance.
  • the separator 5 is in form of a rectangle.
  • the inlet 12 and the outlet 13 are arranged at opposite sides of the rectangle.
  • the rectangle has rounded corners, so that each flow path comprises two curvatures 19, 20 (for flow path 14) and 21, 22 (for flow path 15).
  • a space 23 within the rectangle is kept free from tubes.
  • the inlet 12 is arranged in vertical direction at the upper end of the connecting tube 9. Since the inlet 12 is arranged in the axis of symmetry of the separator 5, the separator 5 is symmetric with respect to a plane intersecting the connecting tube 9.
  • Coalescing means 24 and/or impingement means 25 are arranged in a region at the inlet. Other locations are possible.
  • refrigerant comes out of the refrigerant outlet 8 of the first heat exchanger 2 or evaporator.
  • the flow of refrigerant having a liquid phase and a gaseous phase is guided through the separator 5.
  • the separator 5 the refrigerant flow flows along the two flow paths 14, 15. Due to the fact that two flow paths 14, 15 are arranged in parallel, the velocity of the refrigerant flow is reduced so that liquid refrigerant can separate from the gaseous refrigerant. This is supported by the coalescing means 24 and/or the impingement means 25.
  • Liquid refrigerant removed from the refrigerant flow comes to the bottom of the tubes 16, 17. Since the tubes 16, 17 are inclined, the liquid refrigerant flows back to the input 12 and from there to the connecting tube 9, so that it can directly enter the first heat exchanger 2.

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  • 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)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

A refrigerant system (1) is described comprising a refrigerant circuit having a first heat exchanger (2), a compressor (3), a second heat exchanger (4) and a separator (5) connected to a refrigerant outlet of the first heat exchanger.It should be possible to remove liquid from a refrigerant flow even with a limited size of the separator.To this end, the separator (5) comprises at least two flow paths arranged in parallel between an inlet (12) and an outlet (13).

Description

  • The present invention relates to a refrigeration system comprising a refrigerant circuit having a first heat exchanger, a compressor, a second heat exchanger, and a separator connected to an outlet of the first heat exchanger.
  • In such a refrigeration circuit a refrigerant is circulated. Gaseous refrigerant is compressed by the compressor. This leads to an increased temperature. When the compressed refrigerant gas is guided through a heat exchanger, the so-called condenser, it is cooled and changes from the gaseous state to a liquid state. The liquid refrigerant is then supplied to the other heat exchanger, the so-called evaporator. In the evaporator the refrigerant is evaporated while drawing heat from the ambient air or any other fluid, so that the ambient air is cooled. The refrigerant leaving the evaporator returns to the suction side of the compressor.
  • The refrigerant leaving the evaporator or first heat exchanger is in many cases not fully gaseous. It contains as well refrigerant in liquid form. The liquid phase of the refrigerant may be up to 30 % of the whole refrigerant leaving the evaporator. This liquid refrigerant must be removed from the refrigerant flow in order to avoid a situation in which liquid enters the compressor. Liquid entering the compressor can damage or destroy the compressor. To this end, the separator is used.
  • In some applications the space available for the separator is limited. Thus, the size of the separator is limited as well. This makes it difficult to reliably remove all liquid from the refrigerant flow.
  • The object underlying the invention is to remove liquid from the refrigerant flow even with limited size of the separator.
  • This object is solved with a refrigeration system as described at the outset in that the separator comprises at least two flow paths arranged in parallel between an inlet and an outlet.
  • Such a design has more than one flow path in the separation zone. The use of two or more flow paths arranged in parallel has the effect that the velocity of the refrigerant flow is decreased so that the liquid has more time to "fall" out of the refrigerant flow. Thus, the length of the flow path can be reduced correspondingly. Furthermore, when the flow paths have a circular section, the diameter of this section can be reduced and correspondingly the height of the separator can be kept small while maintaining the same area of the flow paths.
  • In an embodiment of the invention the flow paths are inclined in the same direction from the inlet to the outlet. In other words, the outlet is arranged in a position higher than the position of the inlet in the direction of gravity. Thus, liquid refrigerant removed from the refrigerant flow can flow back in direction towards the inlet under the action of gravity. Thus, the liquid refrigerant can be removed from the separator.
  • In an embodiment of the invention the flow paths have the same angle of inclination. Such an angle can be rather small, for example 5° or 10°. Liquid removed from the refrigerant flow has the same conditions in all flow paths to flow back to the input.
  • In an embodiment of the invention the flow paths have the same lengths. This is a simple design to make the flow resistance in all flow paths equal or almost equal.
  • In an embodiment of the invention the separator is symmetrical with respect to a line connecting the inlet and the outlet. In such a construction the flow through the flow paths can be made the same through all flow paths.
  • In an embodiment of the invention each flow path comprises at least one curvature. Such a curvature provides a benficial flow path for the separation. The creation of turbulence is avoided or at least reduced helping the separation of the gaseous and the liquid refrigerant.
  • In an embodiment of the invention the number of flow paths is two. Although this is a rather small number, the area available for the flow is sufficient to pass the refrigerant flow with a velocity which is low enough to give the refrigerant liquid enough time to fall out of the flow.
  • In an embodiment of the invention the flow paths are arranged in tubes, wherein the tubes surround a tube free space. The tubes form a kind of "donut", which is a simple constructional solution.
  • In an embodiment of the invention the tubes are arranged in form of a rectangle, wherein the inlet and the outlet are arranged at opposite sides of the rectangle. The rectangle will have rounded or squared corners. Such a rectangle form of the separator can easily be made by using generally available semi-finished products.
  • In an embodiment of the invention the first heat exchanger comprises a refrigerant inlet connected to a connecting pipe and a refrigerant outlet connected to the connecting pipe, wherein the inlet of the separator is connected to the connecting pipe. Refrigerant in liquid form can be supplied to the connecting pipe up to a certain level. This has the effect that the same level of liquid refrigerant is available within the first heat exchanger. This refrigerant is at least partly evaporated in the first heat exchanger and escapes at the refrigerant outlet. From there, the refrigerant flow consisting of a gaseous phase and of a liquid phase enters the separator. Liquid refrigerant removed from the refrigerant flow in the separator can flow back to the connecting pipe.
  • In an embodiment of the invention the connecting pipe is arranged in parallel to the direction of gravity. Thus, the connecting pipe is arranged vertically. Liquid refrigerant removed from the refrigerant flow can directly flow down to the refrigerant inlet of the first heat exchanger.
  • In an embodiment of the invention coalescing means are arranged in a region at the inlet. Thus, the refrigerant flow is guided through the coalescing means. The coalescing means have the effect that liquid droplets contained in the refrigerant flow combine into larger drops or droplets so that it is easier to remove these droplets.
  • In an embodiment of the invention the coalescing means comprise a mesh, preferablymade of metal. Other materials are possible. This is a simple design of coalescing means.
  • In addition or alternatively, impingement means are arranged in a region at the inlet. Impingement means can be formed by a surface which is arranged perpendicular or almost perpendicular to a flow direction of the refrigerant flow. Thus, drops of liquid refrigerant hit the surface and can be removed from the surface by gravity.
  • The invention is now described in more detail with reference to the drawing, wherein:
    • Fig. 1
    shows a schematic illustration of a refrigeration system,
    Fig. 2
    shows a front view of a heat exchanger with separator and
    Fig. 3
    shows a top view of the separator.
  • Fig. 1 schematically shows a refrigeration system 1 comprising a refrigerant circuit having a first heat exchanger 2, a compressor 3, a second heat exchanger 4 and a separator 5.
  • Furthermore, in the embodiment shown, the refrigerant circuit comprises an accumulator 6.
  • The first heat exchanger 2 is a plate heat exchanger. However, other types of heat exchangers can be used. The first heat exchanger comprises a refrigerant inlet 7 and a refrigerant outlet 8. A connecting pipe 9 is connected to the refrigerant inlet 7 and to the refrigerant outlet 8. The connecting pipe 9 comprises an oil drain 10. Furthermore, the connecting pipe 9 comprises an expansion valve 11 through which refrigerant in liquid form from the accumulator 6 can be supplied into the connecting pipe 9. The expansion valve can be of a float type or another type, controlled by a liquid level measurement.
  • The connecting pipe 9 is oriented in vertical direction (corresponding to the direction of gravity). The liquid level in the connecting pipe 9 is controlled to provide a driving force to move refrigerant through the heat exchanger.The liquid refrigerant in the first heat exchanger 2 evaporates. The evaporation needs substance to be cooled, which could be heat which is withdrawn from another fluid circulating through a secondary side of the first heat exchanger 2, a product contained in the first heat exchanger 2 or from ambient air around the first heat exchanger 2. The column of liquid refrigerant within the connecting pipe 9 drives the refrigerant out of the refrigerant outlet 8 to an upper part of the column 9. However, this refrigerant flow is not in all cases totally gaseous. In most cases it comprises a gaseous phase and a liquid phase. However, the liquid phase must not arrive at the compressor 3, since the compressor 3 can be damaged or destroyed, when liquid enters the compressor 3.
  • The compressor 3 compresses the gaseous refrigerant. This compression leads to an elevated temperature and pressure of the gaseous refrigerant. The gaseous refrigerant with elevated temperature is guided through the second heat exchanger 4, wherein the heat of the gaseous refrigerant is transferred to a secondary fluid, such as the ambient air, water or glykol. The temperature of the refrigerant is lowered and the refrigerant is liquified and guided to the accumulator 6.
  • In order to remove the liquid phase from the refrigerant flow before the refrigerant flow enters the compressor 3, the separator 5 is used.
  • The separator 5 comprises an inlet 12 connected to the connecting tube 9 and an outlet 13 connected to the compressor 3.
  • As can be seen in Fig. 3, the separator 5 is in form of a donut, i.e. it forms a rectangle having rounded corners. More precisely, the separator provides two flow paths 14, 15. The flow path 14 is arranged within a tube 16 and the flow path 15 is arranged within a tube 17. Both tubes 16, 17 are connected in the region of the inlet 12 and in the region of the outlet 13. Both tubes 16, 17 have the same length and are inclined upwardly from the inlet 12 towards the outlet 13. The angle of inclination for both tubes 16, 17 is the same. This angle is in a region from 1° to 20°.
  • The separator 5 is symmetrical with respect to a line 18 connecting the inlet 12 and the outlet 13. This means that both flow paths 14, 15 have the same flow resistance.
  • As mentioned above, the separator 5 is in form of a rectangle. The inlet 12 and the outlet 13 are arranged at opposite sides of the rectangle. The rectangle has rounded corners, so that each flow path comprises two curvatures 19, 20 (for flow path 14) and 21, 22 (for flow path 15). A space 23 within the rectangle is kept free from tubes.
  • The inlet 12 is arranged in vertical direction at the upper end of the connecting tube 9. Since the inlet 12 is arranged in the axis of symmetry of the separator 5, the separator 5 is symmetric with respect to a plane intersecting the connecting tube 9.
  • Coalescing means 24 and/or impingement means 25 are arranged in a region at the inlet. Other locations are possible.
  • When the refrigeration system 1 is operated, refrigerant comes out of the refrigerant outlet 8 of the first heat exchanger 2 or evaporator. The flow of refrigerant having a liquid phase and a gaseous phase is guided through the separator 5. In the separator 5 the refrigerant flow flows along the two flow paths 14, 15. Due to the fact that two flow paths 14, 15 are arranged in parallel, the velocity of the refrigerant flow is reduced so that liquid refrigerant can separate from the gaseous refrigerant. This is supported by the coalescing means 24 and/or the impingement means 25.
  • Liquid refrigerant removed from the refrigerant flow comes to the bottom of the tubes 16, 17. Since the tubes 16, 17 are inclined, the liquid refrigerant flows back to the input 12 and from there to the connecting tube 9, so that it can directly enter the first heat exchanger 2.
  • If this is not desired, it is of course possible to use additional piping to connect a liquid drain of the separator 5 with a position in the refrigerant system downstream the compressor 3.

Claims (14)

  1. Refrigeration system (1) comprising a refrigerant circuit having a first heat exchanger (2), a compressor (3), a second heat exchanger (4), and a separator (5) connected to a refrigerant outlet (8) of the first heat exchanger (2), characterized in that the separator (5) comprises at least two flow paths (14, 15) arranged in parallel between an inlet (12) and an outlet (13).
  2. Refrigeration system according to claim 1, characterized in that the flow paths (14, 15) are inclined in the same direction from the inlet (12) to the outlet (13).
  3. Refrigeration system according to claim 2, characterized in that the flow paths (14, 15) have the same angle of inclination.
  4. Refrigeration system according to any of claims 1 to 3, characterized in that the flow paths (14, 15) have the same length.
  5. Refrigeration system according to any of claims 1 to 4, characterized in that the separator (5) is symmetrical with respect to a line (18) connecting the inlet (12) and the outlet (13).
  6. Refrigeration system according to any of claims 1 to 5. characterized in that each flow path (14, 15) comprises at least one curvature (19-22).
  7. Refrigeration system according to any of claims 1 to 6, characterized in that the number of flow paths (14, 15) is two.
  8. Refrigeration system according to claim 7, characterized in that the flow paths (14, 15) are arranged in tubes (16, 17), wherein the tubes (16, 17) surround a tube free space (23).
  9. Refrigeration system according to claim 8, characterized in that the tubes (16, 17) are arranged in form of a rectangle, wherein the inlet (12) and the outlet (13) are arranged at opposite sides of the rectangle.
  10. Refrigeration system according to any of claims 1 to 9, characterized in that the first heat exchanger (2) comprises a refrigerant inlet (7) connected to a connecting pipe (9) and the refrigerant outlet (8) is connected to the connecting pipe (9), wherein the inlet (12) of the separator (5) is connected to the connecting pipe (9).
  11. Refrigeration system according to claim 10, characterized in that the connecting pipe (9) is arranged in parallel to the direction of gravity.
  12. Refrigeration system according to any of claims 1 to 11, characterized in that coalescing means (24) are arranged in a region at the inlet (12).
  13. Refrigeration system according to claim 12, characterized in that the coalescing means (24) comprise a mesh made of metal.
  14. Refrigeration system according to any of claims 1 to 13, characterized in that impingement means (25) are arranged in a region at the inlet.
EP19192999.1A 2019-08-22 2019-08-22 Refrigeration system Withdrawn EP3783281A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP19192999.1A EP3783281A1 (en) 2019-08-22 2019-08-22 Refrigeration system
CN202080059151.8A CN114270117A (en) 2019-08-22 2020-08-19 Refrigeration system
US17/635,404 US20220275986A1 (en) 2019-08-22 2020-08-19 Refrigeration system
PCT/EP2020/073269 WO2021032810A1 (en) 2019-08-22 2020-08-19 Refrigeration system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19192999.1A EP3783281A1 (en) 2019-08-22 2019-08-22 Refrigeration system

Publications (1)

Publication Number Publication Date
EP3783281A1 true EP3783281A1 (en) 2021-02-24

Family

ID=67734490

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19192999.1A Withdrawn EP3783281A1 (en) 2019-08-22 2019-08-22 Refrigeration system

Country Status (4)

Country Link
US (1) US20220275986A1 (en)
EP (1) EP3783281A1 (en)
CN (1) CN114270117A (en)
WO (1) WO2021032810A1 (en)

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WO1996009512A1 (en) * 1994-09-23 1996-03-28 Kozinski Richard C Integral evaporator and suction accumulator
WO2009061268A1 (en) * 2007-11-05 2009-05-14 Alfa Laval Corporate Ab Liquid separator for an evaporator system
EP2450646A1 (en) * 2010-11-08 2012-05-09 Honeywell International, Inc. Integrated evaporator and accumulator for refrigerant systems

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GB423158A (en) * 1933-08-16 1935-01-25 Linde Eismasch Ag Evaporator for refrigerating machines
JP3163312B2 (en) * 1994-10-06 2001-05-08 三菱電機株式会社 Accumulator for refrigeration cycle and method for producing the same
JPH0875319A (en) * 1994-08-31 1996-03-19 Sanyo Electric Co Ltd Refrigerating device
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