SE544732C2 - A reversible refrigeration system - Google Patents

A reversible refrigeration system

Info

Publication number
SE544732C2
SE544732C2 SE2050399A SE2050399A SE544732C2 SE 544732 C2 SE544732 C2 SE 544732C2 SE 2050399 A SE2050399 A SE 2050399A SE 2050399 A SE2050399 A SE 2050399A SE 544732 C2 SE544732 C2 SE 544732C2
Authority
SE
Sweden
Prior art keywords
heat exchanger
refrigerant
pay load
way valve
dhe
Prior art date
Application number
SE2050399A
Other languages
Swedish (sv)
Other versions
SE2050399A1 (en
Inventor
Sven Andersson
Tomas Dahlberg
Original Assignee
Swep Int Ab
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 Swep Int Ab filed Critical Swep Int Ab
Priority to SE2050399A priority Critical patent/SE544732C2/en
Publication of SE2050399A1 publication Critical patent/SE2050399A1/en
Publication of SE544732C2 publication Critical patent/SE544732C2/en

Links

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
    • F25B13/00Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B25/00Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B40/00Subcoolers, desuperheaters or superheaters
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0093Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • F25B2339/00Details of evaporators; Details of condensers
    • F25B2339/04Details of condensers
    • F25B2339/047Water-cooled condensers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F28D2021/0063Condensers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F28D2021/0064Vaporizers, e.g. evaporators

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

A reversible refrigeration system comprises a compressor (C) arranged to compress gaseous refrigerant, a four way valve (FWV) switchable between a heating position in which a pay load is heated and a cooling position in which the pay load is cooled. A pay load heat exchanger (PLHE) is connected to the pay load requiring heating or cooling, a dump heat exchanger (DHE), two one way valves (OWV1, OWV2), and two controllable expansion valves (EXPV1, EXPV2), wherein the oneway valves (OWV1, OWV2) each are connected parallel to a corresponding expansion valve, wherein switching of the four-way valve between the heating position and the cooling position controls a flow of pressurized refrigerant to either of the pay load heat exchanger (PLHE) or the dump heat exchanger (DHE) and wherein the heat exchanger which receives the flow of pressurized refrigerant functions as a condenser and the other heat exchanger functions as an evaporator. The dump heat exchanger (DHE), when the four-way valve is in the heating position, is connected to a suction gas heat exchanger arranged to exchange heat between liquid high pressure refrigerant having exited the pay load heat exchanger (PLHE) when the pay load heat exchanger (PLHE) functions as a condenser and low pressure gaseous refrigerant having exited the dump heat exchanger (DHE). The dump heat exchanger (DHE) is arranged to exchange heat between the refrigerant and a heat carrier to which heat can be dumped in a co-current mode.

Description

The present invention relates to a reversible refrigeration system comprising a Compressor arranged to compress gaseous refrigerant, a four way valve switchable between a heating position in which a pay load is heated and a cooling position in which the pay load is cooled, a pay load heat exchanger connected to the pay load requiring heating or cooling, a dump heat exchanger, two one way valves, and two controllable expansion valves, wherein the one-way valves each are connected parallel to a corresponding expansion valve, wherein switching of the four-way valve between the heating position and the cooling position controls a flow of pressurized refrigerant to either of the pay load heat exchanger or the dump heat exchanger and wherein the heat exchanger which receives the flow of pressurized refrigerant functions as a condenser and the other heat exchanger functions as an evaporator.
PRIOR ART In the art of refrigeration, so-called “suction gas heat exchange” is a way to improve e. g. stability of a refrigeration system. In short, suction gas heat exchange is achieved by providing for a heat exchange between warrn liquid, high pressure refrigerant from a condenser outlet and cold gaseous refrigerant from an evaporator outlet. By the suction gas heat exchange, the temperature of the cold gaseous refrigerant will increase, while the temperature of the warrn liquid will decrease. This has two positive effects: Firstly, problems with flash boiling after the warrn liquid has passed a subsequent expansion valve will decrease; Secondly, the risk of droplets in the gaseous refrigerant leaving the evaporator will decrease.
Suction gas heat exchanging is well known. Often, suction gas heat exchange is achieved by simply brazing or soldering pipes carrying refrigerant in the states between which heat exchange is desired to one another. This way of achieving the heat exchange is, however, costly in terms of refrigerant volume required - it is always benef1cial if the piping between different components of a refrigeration system is as short as possible. Suction gas heat exchange by brazing or soldering piping carrying fluids having different temperatures together necessitates longer piping than otherwise would be the case - hence, the intemal volume of the piping will increase, requiring more refrigerant in the refrigeration system. This is detrimental not only from an economical point of view, but also since the amount of refrigerant is limited in several jurisdictions.
Another option is to provide a separate heat exchanger for the suction gas heat exchange. Separate heat exchangers are more efficient than simply brazing different piping portions to one another, but the provision of a separate heat exchanger also necessitates piping connecting the evaporator and the condenser to the suction gas heat exchanger, which piping will increase the refrigerant volume of the refrigeration system.
Moreover, refrigeration systems are often required to being able to operate in both heating mode and in chiller mode, depending on the required/ desired load. Usually, the shift between heating and chilling mode is achieved by shifting a four-way valve such that an evaporator becomes a condenser and a condenser becomes an evaporator. Unfortunately, this means that the heat exchange in either or both the condenser/evaporator units will be a co-current heat exchange, i.e. a heat exchange wherein the media to exchange heat travels in the same general direction, in either heating or cooling mode. As well known by persons skilled in the art, a co-current heat exchange is inferior to a counter-current heat exchange. In evaporators, a decrease of heat exchanging performance might lead to an increased risk of droplets in the refrigerant vapor that leaves the heat exchanger. Such droplets might seriously damage a compressor and are thus highly undesirable. However, devices to shift the flow direction of the medium to exchange heat with the refrigerant in the evaporator are costly and add complexity to the refrigeration system.
It is the object of the present invention to solve or at least mitigate the above and other problems.
SUMMARY OF THE INVENTION According to the invention, the above and other problems are so lved, or at least mitigated, by reversible refrigeration system comprising a compressor arranged to compress gaseous refrigerant, a four way valve switchable between a heating position in which a pay load is heated and a cooling position in which the pay load is cooled, a pay load heat exchanger connected to the pay load requiring heating or cooling, a dump heat exchanger, two one way valves, and two controllable expansion valves, wherein the one-way valves each are connected parallel to a corresponding expansion valve, wherein switching of the four-way valve between the heating position and the cooling position controls a flow of pressurized refrigerant to either of the pay load heat exchanger or the dun1p heat exchanger hv ttte f rst, täxtïaattsitzrt, flvašfvf: hehw closed, the first one-wfaxf *zatve Éneim: open. the seem/td expansion *valve ibeittg open and the sectmd onewtfasf fifalve ibeitts: closed in the lteatiitg position of the fouvi-»vsfav *aalvet and ibv the first -extaatítsittn *vtalve bfzirtg open the first onfz-v/avf valve heting elosedt lhf: sfzcohd ttxtfsztrtsittt: *valve htfirtt: ttlesetí :md the stfcettd etteßtvavf valve being eheh sin the eeolitw ptssitiott of the four-wav ve. and wherein the heat exchanger which receives the flow of pressurized refrigerant functions as a condenser and the other heat exchanger functions as an evaporator, characterized in that the dunip heat exchanger when the four-way valve is in the heating position is connected to a suction gas heat exchanger arranged to exchange heat between liquid high pressure refrigerant having exited the pay load heat exchanger when the pay load heat exchanger filnctions as a condenser and low pressure gaseous refrigerant having exited the dunip heat exchangetj, ahelein that the dunip heat exchanger is arranged to exchange heat between the refrigerant and a heat carrier to which heat can be duniped in a co-current mode, *stfheteitt tthe suction gas .heat exchanfier is integrated in the dumt» heat exchaiigei' and is inactivated en the four *vvav vfalxfe is in tlitä coolirtg position..
Due to provision of one-way valves in the refrigeration system, the suction gas heat exchanger is inactivated when the four way valve is in the heat-ittg--eoatlittg-flg' position.
BREF DESCRIPTION OF THE DRAWINGS In the following, the invention will be described with reference to appended drawings, wherein: Fig. la is a plan view of a heat exchanger according to one en1bodin1ent of the present invention; Fig. lb is a section view of the heat exchanger of Fig. la taken along the line A-A; Fig. lc is a section view of the heat exchanger of Fig. la taken along the line B-B; Fig. 2 is an exploded perspective view of the heat exchanger of Fig. l; Fig. 3 is an exploded perspective view of a heat exchanger according to another en1bodin1ent of the present invention, Fig. 4 is an exploded perspective view of heat exchanger according to another en1bodin1ent of the present invention; Fig 5 is an exploded perspective view of a heat exchanger according to another embodiment of the present invention; Fig. 6 is a schematic view of one embodiment of a reversible refrigeration system shown in a heating mode;_g=¿.=fiï._gfí_ Fig. 7 is a schematic view of the reversible refrigeration system of Fig. 6 shown in a cooling modeç, lïf-ig-.---fF-l»-å*s--a»se-helfnatzíe--view-of-ainotheïf--elfnbar-sifilfnent-ef-a-felaersi-ble--reffí-geafiaition sylsteiæig--aiid E-'T Q 1' 1 fi C' 1hfÄ-1ÅÜ'\ Y çfÄ- Y \'$\{':'\ h + i " 1 n. . :vv u: nu i Li. s ar 4) wrw n* ca m r+r_\'~ '\c\1»\f11»\1^'rr_\'~l 1.1 1 u n :l I no u, 0 nvnziu/Llv v u; livat, mAx-lxuinöfi-L EJ ML s; vyn: .uiøvx/z, ai; t :six/LL DESCRIPTION OF EMBODIMENTS In Figs. 1a-2, a brazed heat exchanger 100 having a second heat exchanging portion usable as an integrated suction gas heat exchanger portion is shown. The heat exchanger 100 is made from sheet metal plates 1 10a-10h stacked in a stack to forrn the heat exchanger 100 and provided with a pressed pattern of ridges R and grooves G adapted to keep the plates on a distance from one another under forrnation of interplate flow channels for media to exchange heat. Large port openings 02 and 03 are provided near corners of each heat exchanger plate, whereas large openings 01 and 04 are provided centra11y close to a short side of each heat exchanger plate. Areas surrounding the port openings 01 to 04 are provided at different heights such that selective communication between the port openings and the interplate flow channels is achieved. In the heat exchanger 100, the areas surrounding the port openings are arranged such that the large openings 01 and 02 are in fluid communication with one another by some plate interspaces, whereas the openings 03 and 04 are in fluid communication with one another by neighboring plate interspaces.
The heat exchanger plates 110a-110h are also provided with a dividing surface DW extending from one long side of each heat exchanger plate to the other longside thereof The heat exchanger plate 110h is not provided with port opening. This is in order to provide a seal for the port openings, such that fluid introduced at one end of the plate stack does not immediately escape the plate pack at the other sided thereof With special reference to Fig. 2, a number of heat exchanger plates 210a - 210h are shown. Each of the heat exchanger plates, except the heat exchanger plate 210h, is provided With port openings 01, 02, 03, 04, S01 and S02. The port openings are surrounded by areas provided at different levels, such that selective communication is provided between the port openings and the interplate flow channels forrned between neighbouring heat exchanger plates, as mentioned above. Moreover, each of the heat exchanger plate is surrounded by a skirt S, which extends generally perpendicular to a plane of the heat exchanger plate and is adapted to contact skirts of neighbouring plates in order to provide a seal along the circumference of the heat exchanger.
In order to seal the interplate flow channel for brine flow between the large port opening 04 and 03, a dividing surface DS is provided between long sides of the heat exchanger plates. The dividing surface DS comprises an elongate flat surface provided on different heights of different plates; when the surfaces of neighbouring plates contact one another, the channel will be sealed, whereas it will be open if they do not. In the present case, the dividing surface DS is provided at the same height as the areas surrounding the large port openings 01 and 02, meaning that for interplate flow channels fluidly connecting large port openings 01 and 02, the dividing surface will be open, whereas for the flow channel fluidly connecting the large port openings 03 and 04, the dividing surface will block fluid in this plate interspace.
Since the dividing surface will block fluid flow in the plate interspace communicating with the large port openings 03 and 04, there will be separate interplate channels on either side of the dividing surface DS. The interplate flow channel on the side of the dividing surface DS not communicating with the large opening 03 and 04 communicates with two small port opening S01 and S02. It should be noted that the dividing surface DS does not block the interplate flow channels communicating with the large port openings 01 and 02; hence, medium flowing in the interplate flow channels communicating with the small port openings S01 and S02 will exchange heat with med medium flowing in the flow channels communicating with the large openings 01 and 02 - just like medium flowing in the interplate flow channels communicating with the large port openings 03 and In an embodiment shown in Fig. 2, the dividing surface DS extends in a straight line from one longside to the other, passing between large port openings 01 and 04. The small openings S01 and S02 are situated on either sides of the large port opening 01. It should be noted that the large port opening 01 is placed such that medium flowing in the interplate flow channel communicating with the small port openings S01 and S02 may pass on both sides of the large port opening 01. This arrangement is beneficial in that the port opening 01 will have an even temperature along its circumference.
In an embodiment shown in Fig. 3, the dividing surface does not extend in a straight line, but is slightly bent away from the port opening 01, which is placed near a comer of the heat exchanger. This provides for a more uniforrn flow area from the small opening S01 to the small opening S In an embodiment shown in Fig. 4, the dividing portion extends in a semi- circular fashion around the port opening 01. This embodiment is beneficial in that the large port openings 01-04 may be placed close to the comers of the heat exchanger, hence providing for a large heat exchanging area. This embodiment is also beneficial in that the flow area of the interplate flow channel on the side of the dividing surface DS not communicating with the large opening 03 and 04 will have an even cross section all the way between the small opening S01 and the small opening S In Fig__5, an embodiment resembling the embodiment of Fig. 2 is shown. Just like the previously shown embodiment, the dividing surface DS extends in a straight line from one longside of the heat exchanger to the other, passing between large port openings 01 and 04. The small openings S01 and S02 are situated on either sides of the large port opening 01. However, the large port opening 01 is located and arranged such that no fluid may pass between the large port opening 01 and the short side of the heat exchanger. This is beneficial in that the heat exchange between fluid flowing between the small openings S01 and S02 and fluid about to exit the heat exchanger through the large opening 01 is improved, since the “dead area” between the port opening 01 and the short side of the heat exchanger is avoided.
In Figs. 6 and 7, a preferred embodiment of a chiller system that can use a heat exchanger according to any of the above heat exchanger embodiments is shown in in heating mode and cooling mode, respectively.
The chiller system according to the first embodiment comprises a compressor C, a four-way valve FWV, a pay load heat exchanger PLHE connected to a brine system requiring heating or cooling, a first controllable expansion valve EXPV1, a first one- way valve 0V1, a dump heat exchanger DHE connected to a heat source to which undesired heat or cold could be dumped, a second expansion valve EXPV2 and a second one-way valve 0WV2. The heat exchangers PLHE and DHE are each provided with the four large openings 01-04 as disclosed above and the two small openings S01 and S02, wherein the large openings 01 and 02 of each heat exchanger communicate with one another, the large openings 03 and 04 of each heat exchanger communicate with one another and wherein the small openings S01 and S02 of each heat exchanger communicate with one another. Heat exchange will occur between fluids flowing from 01 to 02 and fluids flowing between 03 and 04 and S01 and S02. There will, however, be no heat exchange between fluids flowing from 03 to 04 and fluids flowing from S01 to S In heating mode, shown in Fig. 6, the compressor C will deliver high pressure gaseous refrigerant to the four-way valve FWV. In this heating mode, the four-way valve is controlled to convey the high pressure gaseous refrigerant to the large opening 01 of the pay load heat exchanger PLHE. The high pressure, gaseous refrigerant will then pass the pay load heat exchanger PLHE and exit at the large opening 02. While passing the pay-load heat exchanger PLHE, the high pressure gaseous refrigerant will exchange-if heat with a brine solution connected to a pay-load requiring heating and flowing from the large opening 04 to the large opening 03, i.e. in a counterflow direction compared to the refrigerant, which flows from the large opening 01 to the large opening 02. While exchanging heat with the brine solution, the high pressure gaseous refrigerant will condense, and when exiting the Pay-load heat exchanger PLHE through the large opening 02, it will be fully condensed, i.e. be in the liquid state.
In the heating mode, the first expansion valve EXPV1 will be fully closed, and the flow of liquid refrigerant exiting the pay-load heat exchanger will pass the first one- way valve 0WV1, which allows for a refrigerant flow in this direction, while it will block flow in the other direction (which will be explained later in connection to the description of the cooling mode).
After having passed the first one-way valve 0WV1, the liquid refrigerant (still comparatively hot) will enter the small opening S02 of the dump heat exchanger DHE, and exit the heat exchanger through the small opening S01. During the passage between the small openings S02 and S01, the temperature of the refrigerant will drop signif1cantly due to heat exchange with cold, primarily gaseous refrigerant about to exit the dump heat exchanger DHE.
After leaving the dump heat exchanger DHE through the small opening S01, the liquid refrigerant will pass the second expansion valve EXPV2, where the pressure of the refrigerant will drop, causing flash boiling of some of the refrigerant, which will cause the temperature to drop. From the second expansion valve, the refrigerant will pass a branch connected to both the second one-way valve 0WV2, which is connected between the high pressure side and the low pressure side of the refrigerant circuitry and closed for refrigerant flow due to the pressure difference between the high pressure side and the low pressure side. After having passed the branch, the cold, low pressure semi liquid refrigerant will enter the large opening 02 and pass the dump heat exchanger DHE under heat exchange with a brine solution connected to a source from which low temperature heat can be collected, eg. an outside air collector, a solar collector or a hole drilled in the ground. Due to the heat exchange with the brine solution, which flows from the large opening 04 to the large opening 03, the primarily liquid refrigerant will vaporize. The heat exchange between the brine solution and the refrigerant will take place under co-current conditions, which is well known to give an inferior heat exchange performance as compared to counter-current heat exchange.
Just prior to the exiting the dump heat exchanger DHE through the large opening 01, the refrigerant (now almost completely vaporized) will exchange heat with the comparatively hot, liquid refrigerant that entered the dump heat exchanger through the small opening S02 and exited the dump heat exchanger through the small port opening S01. Consequently, the temperature of the refrigerant about to exit the dump heat exchanger DHE through the opening 01 will increase, hence ensuring that all of this refrigerant is completely vaporized.
It is well known by persons skilled in the art that co-current heat exchange is inferior to counter-current heat exchange. However, due to the provision of the heat exchange between the relatively hot liquid brine entering the small opening S02 and the mainly gaseous refrigerant about to leave the dump heat exchanger DHE (i.e. a so- called “suction gas heat exchange”), it is not necessary to vaporize the refrigerant completely during the brine-refrigerant heat exchange. Instead, the refrigerant may be only semi-vaporized when it enters the suction gas heat exchange with the hot liquid refrigerant, since the remaining liquid phase refrigerant will evaporate during this heat exchange. It is well known that liquid-to-liquid heat exchange is much more efficient than Gas-to-liquid heat exchange.
From the opening 01 of the dump heat exchanger, the gaseous refrigerant will enter the four-way valve FWV, which is controlled to direct the flow of gaseous refrigerant to the compressor, in which the refrigerant is compressed again.
In Fig. 7, the chiller system is shown in cooling mode. In order to switch mode from heating mode to cooling mode, the four-way valve FWV is controlled such that the compressor feeds compressed gaseous refrigerant to the opening 01 of the dump heat exchanger DHE. The expansion valve EXPV2 will be entirely closed, the one-way valve 0WV2 will be open, the one-way valve 0WVl will be closed and the expansion valve EXPVl Will be open to control the pressure before and after the refrigerant has passed the expansion valve EXPVl.
Hence, in cooling mode, the dun1p heat exchanger Will function as a co-current condenser, and the “suction gas heat exchanger” thereof Will not perforrn any heat exchange, Whereas the pay-load heat exchanger PLHE Will function as a co-current condenser. However, due to the provision of the suction gas heat exchange between the hot liquid refrigerant and sen1i-vaporised refrigerant about to leave the pay-load heat exchanger PLHE, the efficiency of the co-current heat exchange can be n1aintained at acceptable levels.
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Claims (3)

1. A reVersible refrigeration system con1prising a Compressor (C) arranged to conipress gaseous refrigerant, a four way Valve (FWV) switchable between a heating position in which a pay load is heated and a cooling position in which the pay load is cooled, a pay load heat exchanger (PLHE) connected to the pay load requiring heating or cooling, a dun1p heat exchanger (DHE), two one way Valves (OWV1, OWV2), and two controllable expansion Valves (EXPV1, EXPV2), wherein the one-way Valves (OWV1, OWV2) each are connected parallel to a corresponding expansion Valve, wherein switching of the four-way Valve between the heating position and the cooling position controls a flow of pressurized refrigerant to either of the pay load heat exchanger (PLHE) or the dun1p heat exchanger (DHE) by the first expansion Valve (EXPV1) being closed, the first one-way valve (OWV1) being open, the second expansion valve (EXPV2) being open and the second one-way Valve (OWV2) being closed in the heating position of the four-way Valve (FWV), and by the first expansion Valve (EXPV1) being open, the first one-way Valve (OWV1) being closed, the second expansion Valve (EXPV2) being closed and the second one-way Valve (OWV2) being open in the cooling position of the four-way Valve (FWV), and wherein the heat exchanger which receives the flow of pressurized refrigerant fianctions as a condenser and the other heat exchanger fianctions as an eVaporator, characterized in that the dun1p heat exchanger (DHE) when the four way Valve is in the heating position is connected to a suction gas heat exchanger arranged to exchange heat between liquid high pressure refrigerant having exited the pay load heat exchanger (PLHE) when the pay load heat exchanger (PLHE) fianctions as a condenser and low pressure gaseous refrigerant having exited the dun1p heat exchanger (DHE), in that the dun1p heat exchanger (DHE) is arranged to exchange heat between the refrigerant and a heat carrier to which heat can be duniped in a co-current n1ode, wherein the suction gas heat exchanger is integrated in the dun1p heat exchanger (DHE) and is inactiVated when the four way Valve (FWV) is in the cooling position.
2. The reversible refrigeration system of claini 1, Wherein a second Suction gas heat exchanger is arranged to exchange heat between liquid refrigerant having exited the dun1p heat exchanger (DHE) and gaseous refrigerant having exited the pay load heat exchanger (PLHE) When the four Way Valve (FWV) is in the cooling position.
3. The reversible refrigeration systeni of claini 2, Wherein the second suction gas heat exchanger is integrated in the pay load heat exchanger (PLHE).
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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080173034A1 (en) * 2007-01-19 2008-07-24 Hallowell International, Llc Heat pump apparatus and method
US20080209930A1 (en) * 2005-12-16 2008-09-04 Taras Michael F Heat Pump with Pulse Width Modulation Control
US20090282861A1 (en) * 2005-09-22 2009-11-19 Daikin Industries, Ltd. Air conditioning apparatus
JP2012112591A (en) * 2010-11-25 2012-06-14 Hisaka Works Ltd Evaporator and refrigeration system equipped with the same
US20150362269A1 (en) * 2013-02-14 2015-12-17 Swep International Ab Port opening with supercooling
US20160153687A1 (en) * 2014-12-01 2016-06-02 David Deng Additive heat unit for hvac heat pump system
WO2017029534A1 (en) * 2015-08-19 2017-02-23 Carrier Corporation Reversible liquid suction gas heat exchanger

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090282861A1 (en) * 2005-09-22 2009-11-19 Daikin Industries, Ltd. Air conditioning apparatus
US20080209930A1 (en) * 2005-12-16 2008-09-04 Taras Michael F Heat Pump with Pulse Width Modulation Control
US20080173034A1 (en) * 2007-01-19 2008-07-24 Hallowell International, Llc Heat pump apparatus and method
JP2012112591A (en) * 2010-11-25 2012-06-14 Hisaka Works Ltd Evaporator and refrigeration system equipped with the same
US20150362269A1 (en) * 2013-02-14 2015-12-17 Swep International Ab Port opening with supercooling
US20160153687A1 (en) * 2014-12-01 2016-06-02 David Deng Additive heat unit for hvac heat pump system
WO2017029534A1 (en) * 2015-08-19 2017-02-23 Carrier Corporation Reversible liquid suction gas heat exchanger

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