WO2009096915A1 - Système réfrigérant à circuit de fluide frigorigène de réchauffement - Google Patents

Système réfrigérant à circuit de fluide frigorigène de réchauffement Download PDF

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Publication number
WO2009096915A1
WO2009096915A1 PCT/US2008/001225 US2008001225W WO2009096915A1 WO 2009096915 A1 WO2009096915 A1 WO 2009096915A1 US 2008001225 W US2008001225 W US 2008001225W WO 2009096915 A1 WO2009096915 A1 WO 2009096915A1
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WO
WIPO (PCT)
Prior art keywords
reheat
refrigerant circuit
refrigerant
evaporator
cooling
Prior art date
Application number
PCT/US2008/001225
Other languages
English (en)
Inventor
Alexander Lifson
Michael F. Taras
Original Assignee
Carrier Corporation
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 Corporation filed Critical Carrier Corporation
Priority to PCT/US2008/001225 priority Critical patent/WO2009096915A1/fr
Priority to US12/864,122 priority patent/US20100307172A1/en
Priority to CN2008801259834A priority patent/CN101932883A/zh
Priority to EP08724970A priority patent/EP2250445A1/fr
Publication of WO2009096915A1 publication Critical patent/WO2009096915A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F24F11/43—Defrosting; Preventing freezing of indoor units
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/06—Removing frost
    • F25D21/12—Removing frost by hot-fluid circulating system separate from the refrigerant system
    • F25D21/125—Removing frost by hot-fluid circulating system separate from the refrigerant system the hot fluid being ambient air

Definitions

  • the present disclosure is related to refrigerant systems. More particularly, the present disclosure is related to refrigerant systems having defrost functionality provided by a reheat refrigerant circuit.
  • Refrigerant systems are utilized to control the temperature and/or humidity of air in various environments to be conditioned.
  • a refrigerant is compressed in a compressor and delivered to a heat rejection heat-exchanger (or, in many cases, an outdoor heat-exchanger).
  • heat rejection heat- exchanger heat is exchanged between outside ambient air and the compressed refrigerant, to remove heat from the compressed refrigerant.
  • the refrigerant passes to an expansion device, in which the refrigerant is expanded to a lower pressure and lower temperature, and then to an evaporator (or, in typical air conditioning installations, an indoor heat-exchanger).
  • an evaporator or, in typical air conditioning installations, an indoor heat-exchanger.
  • heat is exchanged between the now cooled lower pressure refrigerant and the indoor air, to remove heat from the indoor air. In this manner, the evaporator cools the air that is being supplied to the conditioned environment.
  • refrigerant systems also control the humidity level in the conditioned environment.
  • the temperature level of the conditioned air necessary to provide the desired humidity level is lower than the desired temperature of the conditioned air.
  • many refrigerant systems include a reheat coil or heat- exchanger (hereinafter "coil") that is placed in the conditioned air stream downstream of the evaporator. In this manner, the reheat coil reheats the conditioned air after the air has been conditioned (e.g., cooled and dehumidified) in the evaporator.
  • a refrigerant system includes a cooling refrigerant circuit, a reheat refrigerant circuit, an evaporator fan, and a controller.
  • the cooling refrigerant circuit includes an evaporator.
  • the reheat refrigerant circuit includes a reheat coil.
  • the evaporator fan is capable of forcing indoor air in a first direction and a second direction. The indoor air passes across the evaporator before the reheat coil in the first direction but passes across the reheat coil before the evaporator in the second direction.
  • the controller when in a conventional cooling mode, controls the reheat refrigerant circuit so that the reheat refrigerant circuit is not in fluid communication with the cooling refrigerant circuit and controls the evaporator fan to force the indoor air in the first direction. Conversely, the controller, when in a defrost mode, controls the reheat refrigerant circuit so that the reheat refrigerant circuit is in fluid communication with the cooling refrigerant circuit and controls the evaporator fan to force the indoor air in the second direction. In the conventional dehumidification mode the controller controls the reheat refrigerant circuit so that the reheat refrigerant circuit is in fluid communication with the cooling refrigerant circuit and controls the evaporator fan to force the indoor air in the first direction.
  • the refrigerant system includes a cooling refrigerant circuit, a reheat refrigerant circuit, an evaporator fan, and a controller.
  • the cooling refrigerant circuit includes an evaporator.
  • the reheat refrigerant circuit includes a reheat coil.
  • the evaporator fan rotates in a first rotational direction to force indoor air in a first direction and rotates in a second rotational direction to force the indoor air in a second direction.
  • the evaporator is positioned upstream of the reheat coil in the first direction.
  • the controller operates the refrigerant system in a conventional cooling mode when the reheat refrigerant circuit is not in fluid communication with the cooling refrigerant circuit and the evaporator fan rotates in the first rotational direction.
  • the controller also operates the refrigerant system in a defrost mode when the reheat refrigerant circuit is in fluid communication with the cooling refrigerant circuit and the evaporator fan rotates in the second rotational direction.
  • the controller operates the refrigerant system in a conventional dehumidification mode when the reheat refrigerant circuit is in fluid communication with the cooling refrigerant circuit and the evaporator fan rotates in the first rotational direction.
  • the refrigerant system includes a cooling refrigerant circuit, a reheat refrigerant circuit, an evaporator fan that rotates in a single rotational direction, one or more dampers, and a controller.
  • the cooling refrigerant circuit includes an evaporator.
  • the reheat refrigerant circuit includes a reheat coil.
  • the dampers are in a flow path of the indoor air and have two positions. The first position forces the indoor air in a first direction so the indoor air passes across the evaporator before the reheat coil. The second position forces the indoor air in a second direction so the indoor air passes across the reheat coil before the evaporator.
  • the controller operates the refrigerant system in a conventional cooling mode when the reheat refrigerant circuit is not in fluid communication or at least partially isolated from the cooling refrigerant circuit and the one or more dampers are in the first position.
  • the controller also operates the refrigerant system in a defrost mode when the reheat refrigerant circuit is in fluid communication with the cooling refrigerant circuit and the one or more dampers are in the second position.
  • the controller operates the refrigerant system in a conventional dehumidification mode when the reheat refrigerant circuit is in fluid communication with the cooling refrigerant circuit and the one or more dampers are in the first position.
  • FIG. 1 is a schematic depiction of an exemplary embodiment of a refrigerant system according to the present disclosure operating in a normal or conventional cooling mode;
  • FIG. 2 is schematic depiction of the refrigerant system of FIG. 1 operating in a reheat or conventional dehumidification mode
  • FIG. 3 is schematic depiction of the refrigerant system of FIG. 1 operating in a defrost mode
  • FIG. 4 is schematic depiction of an alternate embodiment of the refrigerant system of FIG. 1 operating in the normal mode and the reheat mode;
  • FIG. 5 is schematic depiction of the refrigerant system of FIG. 4 operating in the defrost mode. DETAILED DESCRIPTION OF THE INVENTION
  • FIG. 1 an exemplary embodiment of a refrigerant system according to the present disclosure, generally indicated by reference numeral 10, is shown.
  • Refrigerant system 10 includes a cooling refrigerant circuit 12, a reheat refrigerant circuit 14, and a bypass refrigerant circuit 16.
  • Refrigerant system 10 is configured to utilize reheat refrigerant circuit 14 and bypass refrigerant circuit 16 during the defrosting of the evaporator.
  • Cooling refrigerant circuit 12 includes a compressor 18, a heat rejection heat-exchanger 20, an expansion device 22, and an evaporator 24, all in fluid communication with one another in a known manner to provide, for instance, a cooling or heating function using a known refrigerant (not shown).
  • Refrigerant system 10 further includes a heat rejection heat-exchanger fan 26, an evaporator fan 28, and a refrigerant system controller 30.
  • Reheat refrigerant circuit 14 includes a reheat coil 32 and a first reheat valve 34-1 and a second reheat valve 34-2, while bypass circuit 16 includes a bypass valve 36.
  • the first reheat valve 34-1 typically is a three-way valve and the second reheat valve 34-2 is a check valve.
  • Controller 30 is in electrical communication with the compressor 18, heat rejection heat-exchanger fan 26, evaporator fan 28, first reheat valve 34- 1 , and bypass valve 36. In some embodiments, the controller 30 can also be in electrical communication with the compressor 18, expansion device 22 and/or second reheat valve 34-2. In this manner, the controller 30 is configured to control the operation of the various components of the refrigerant system 10.
  • the controller 30 is configured to operate the refrigerant system 10 in a normal or conventional cooling mode (FIG. 1 ), a reheat or conventional dehumidification mode (FIG. 2), and defrost mode (FIG. 3).
  • Refrigerant system 10 operates in the defrost mode without the need for additional or specialized defrosting devices, such as, for example, an electric heater. Rather, it has been determined by the present disclosure that the refrigerant system 10 can provide the defrost mode of operation by simply making use of the existing components of the reheat refrigerant circuit 14. More particularly, the refrigerant system 10 is configured to control evaporator fan 28 to force air in a first normal direction during the normal mode and the reheat mode of operation, but in a second opposite direction during the defrost mode of operation.
  • the compressor 18 draws in a low-pressure refrigerant 40, in a vapor form and compresses this low-pressure vapor refrigerant into a high pressure and temperature refrigerant 42.
  • the vapor refrigerant flows to the heat rejection heat-exchanger 20.
  • the controller 30 controls the bypass valve 36 to a closed position so that refrigerant 42 flows through the heat rejection heat-exchanger 20 and not through the bypass refrigerant circuit 16.
  • the controller 30 controls the bypass valve 36 so that the bypass refrigerant circuit 16 is not in fluid communication with cooling refrigerant circuit 12 during the normal mode of operation.
  • the heat rejection heat-exchanger 20 acts as a condenser, in the subcritical cycle, or as a gas cooler, in a transcritical cycle, where during heat transfer interaction with a secondary fluid, such as outside or ambient air 44 that is forced across the heat rejection heat-exchanger 20 by the heat rejection heat-exchanger fan 26.
  • a secondary fluid such as outside or ambient air 44 that is forced across the heat rejection heat-exchanger 20 by the heat rejection heat-exchanger fan 26.
  • a secondary fluid such as outside or ambient air 44 that is forced across the heat rejection heat-exchanger 20 by the heat rejection heat-exchanger fan 26.
  • a secondary fluid such as outside or ambient air 44 that is forced across the heat rejection heat-exchanger 20 by the heat rejection heat-exchanger fan 26.
  • a liquid pump may substitute the fan 26 to pump secondary loop liquid performing heat transfer interaction in the heat rejection heat-exchanger 20 instead of the outside or ambient air 44.
  • the refrigerant 46 exits heat rejection heat-exchanger 20 and flows to the expansion device 22.
  • the controller 30 controls the first reheat valve 34-1 to a closed position so that the refrigerant 46 flows through the expansion device 22 and, not, through the reheat refrigerant circuit 14.
  • the controller 30 controls the first reheat valve 34-1 so that the reheat refrigerant circuit 14 is not in fluid communication with the cooling refrigerant circuit 12 during the normal or conventional cooling mode of operation.
  • the second reheat valve 34-2 can be a check valve that ensures the refrigerant 46 does not enter the reheat refrigerant circuit 14.
  • the second reheat valve 34-2 can be in electrical communication with the controller 30, which controls the second reheat valve 34-2 to the closed position during the normal mode of operation to ensure that refrigerant 46 does not enter the reheat refrigerant circuit 14.
  • the expansion device 22 expands refrigerant 46 into a lower pressure, lower temperature, two-phase mixture refrigerant 48, which flows into the evaporator 24.
  • the expansion device 22 is a thermostatic expansion valve or a fixed restriction expansion device, while in other embodiments the expansion device can be an electronic expansion device (EXV) in electrical communication with the controller 30.
  • EXV electronic expansion device
  • the evaporator 24 acts as a heat accepting heat-exchanger where heat transfer interaction occurs between the refrigerant and the indoor air 50 that is forced across the evaporator 24 by the evaporator fan 28 in a first direction 54.
  • the refrigerant 48 is evaporated back into a low pressure vapor refrigerant 40, while the indoor air 50 is cooled and usually dehumidified to provide the conditioned air 52 that is supplied to a climate- controlled space or zone.
  • the vapor refrigerant 40 which is typically in a thermodynamic superheated state, then flows from the evaporator 24 back to the compressor 18.
  • reheat coil 32 is positioned downstream, with respect to the flow of indoor air 50 in the first direction 54 induced by the evaporator fan 28. However, since the reheat valves 34-1 , 34-2 are in the closed position, the flow of conditioned air 52 through the reheat coil 32 does not result in any further conditioning or reheating of this conditioned air.
  • the controller 30 activates the compressor 18, activates the heat rejection heat-exchanger fan 26, closes the bypass valve 36, closes the reheat valves 34-1 and 34-2, activates, when necessary, the expansion valve 22, and activates the evaporator fan 28 to force the indoor air 50 across the evaporator 24 and the reheat coil 32 in the first direction. Since the controller 30 controls the evaporator fan 28 to force indoor air 50 in the first direction 54, the indoor air is forced first across the evaporator 24 then across the reheat coil 32.
  • the refrigerant system 10 is configured to force the indoor air 50 in the first direction 54 by controlling the evaporator fan 28 to rotate in a first rotational direction 56. It has to be pointed out that the evaporator fan 28 may be of a variable speed type so that the controller 30 may also control the speed of the evaporator fan 28 if desired.
  • the refrigerant system 10 operates in substantially the same manner in the reheat mode as in the normal mode, except that the controller 30 controls the first reheat valve 34-1 to an open position so that the refrigerant 46 flows first through the reheat refrigerant circuit 14 and only then through the expansion device 22.
  • the controller 30 controls the first reheat valve 34-1 so that the reheat refrigerant circuit 14 is in fluid communication with the cooling refrigerant circuit 12 during the reheat mode of operation.
  • the compressor 18 draws in a low pressure refrigerant 40, in a vapor form and compresses this low pressure vapor refrigerant into a high pressure and temperature refrigerant 42. From the compressor 18, the vapor refrigerant flows to the heat rejection heat-exchanger 20.
  • the controller 30 may control the bypass valve 36 to a closed or partially/fully open position so that the vapor high pressure and high temperature refrigerant 42 can flow through the heat rejection heat-exchanger 20 and, not, the bypass refrigerant circuit 16, or through both the heat rejection heat-exchanger 20 and bypass refrigerant circuit 16.
  • the controller 30 controls the bypass valve 36 so that the bypass refrigerant circuit 16 may or may not be in fluid communication with the cooling refrigerant circuit 12 during the reheat mode of operation.
  • the controller 30 can control the bypass valve 36 to a partially open position so that a portion of refrigerant 42 flows through the heat rejection heat-exchanger 20 and a remaining portion flows through the bypass refrigerant circuit 16.
  • the heat rejection heat-exchanger 20 acts as a condenser, in a subcritical cycle, or as a gas cooler, in a transcritical cycle, where during heat transfer interaction with outside or ambient air 44 that is forced across the heat rejection heat-exchanger 20 by the heat rejection heat-exchanger fan 26.
  • the vapor refrigerant 42 is desuperheated to the point where it condenses to a liquid refrigerant 46 and is typically subcooled, or just simply cooled from the thermodynamic state 42 to the thermodynamic state 46, in the transcritical applications.
  • a liquid pump may substitute the fan 26 to pump secondary loop liquid performing heat transfer interaction in the heat rejection heat-exchanger 20 instead of the outside or ambient air 44.
  • the refrigerant 46 exits the heat rejection heat-exchanger 20 and flows to the first reheat valve 34-1.
  • the controller 30 controls the first reheat valve 34-1 to an open position so that the refrigerant 46 flows through the reheat coil 32, through the second reheat valve 34-2, and only then into the expansion device 22.
  • the second reheat valve 34-2 can be a check valve that allows the refrigerant 46 to exit the reheat refrigerant circuit 14 back into the cooling refrigerant circuit 12.
  • the second reheat valve 34-2 can be in electrical communication with the controller 30, which controls the second reheat valve 34-2 to the open position during the reheat mode of operation to allow the refrigerant 46 to reenter the cooling refrigerant circuit 12.
  • the heat capacity of the refrigerant 46 can be used to reheat the conditioned air 52 in the manner discussed in more detail below.
  • the expansion device 22 expands the refrigerant 46 into a low pressure, low temperature, two-phase mixture refrigerant 48 and flows into the evaporator 24.
  • the evaporator 24 acts as a heat accepting heat- exchanger where heat transfer interaction occurs between the refrigerant and the indoor air 50 that is forced across the evaporator 24 by the evaporator fan 28.
  • the refrigerant 48 is evaporated back into a low pressure vapor refrigerant 40, while the indoor air 50 is cooled and usually dehumidified to provide the conditioned air 52 that is supplied to a climate-controlled space or zone.
  • the vapor refrigerant 40 which is typically in the superheated thermodynamic state, then flows from the evaporator 24 back to the compressor 18.
  • the reheat coil 32 is positioned downstream, with respect to the flow of indoor air 50 induced by the evaporator fan 28 in the first direction 54. Since the refrigerant 46 is flowing through the reheat coil 32, the flow of conditioned air 52 through the reheat coil 32 results in the reheat coil 32 acting as a heat rejecting heat-exchanger, where heat transfer is taking place from the refrigerant to air re-heating the air, and where the conditioned air 52 is forced across the reheat coil 32 by the evaporator fan 28. In this manner, the conditioned air 52 can be reheated to a desired temperature by the reheat coil 32 while maintaining the desired humidity by the evaporator 24 to provide a reheated air 58.
  • the controller 30 activates the compressor 18, activates the heat rejection heat-exchanger fan 26, controls the bypass valve 36, opens the first reheat valve 34-1 , activates, when necessary, the expansion valve 22, and activates the evaporator fan 28 to force the indoor air 50 across the evaporator 24 and the reheat coil 32 in the first direction 54.
  • the controller 30 controls the evaporator fan 28 to force the air in the first direction 54 so that the indoor air 50 is forced first across the evaporator 24 then across the reheat coil 32 to provide the reheated air 58.
  • the refrigerant system 10 is configured, in the embodiment illustrated in FIG. 2, to force the indoor air 50 in the first direction 54 by controlling the evaporator fan 28 to rotate in the first rotational direction 56.
  • FIG. 2 schematic is exemplary, and any refrigerant system incorporating any other reheat circuit configuration could equally benefit from the disclosure.
  • the refrigerant system 10 operates in substantially the same manner in the defrost mode as in the reheat mode, except that the controller 30 preferably controls the bypass valve 36 to an open position so that at least a portion of the high pressure and temperature refrigerant 42 flows through the bypass refrigerant circuit 16 instead of flowing through the heat rejection heat-exchanger 20 and reverses the direction of flow of the indoor air 50 across the evaporator 24 from a first direction 54 (FIGS. 1 and 2) to a second direction 60 (FIG. 3).
  • bypass refrigerant circuit 16 can be designed such that predominantly all the vapor refrigerant 42 flows through the bypass refrigerant circuit 16, or alternatively, a shutoff solenoid valve (not shown) can be placed upstream of the heat rejection heat-exchanger 20 to prevent any flow of the vapor refrigerant 42 through the heat rejection heat- exchanger 20.
  • the compressor 18 draws in the low pressure refrigerant 40, in a vapor form and compresses this low pressure vapor refrigerant into the high pressure and high temperature refrigerant 42. From the compressor 18, the vapor refrigerant 42 flows towards the heat rejection heat-exchanger 20 and the bypass refrigerant circuit 16.
  • the controller 30 preferably controls the bypass valve 36 to the open position so that at least a portion of the vapor refrigerant 42 does not flow through heat rejection heat-exchanger 20 but rather flows through the bypass refrigerant circuit 16. Further, the controller 30 can, in some embodiments, control the heat rejection heat-exchanger fan 26 to an off state to prevent any active heat exchange between the refrigerant and ambient air in the heat rejection heat-exchanger 20. In this manner, the controller 30 preferably places the bypass refrigerant circuit 16 in fluid communication with the cooling refrigerant circuit 12 during the defrost mode of operation so that the high pressure and high temperature refrigerant 42 flows into the reheat refrigerant circuit 14 providing greater heat capacity during the defrost mode of operation.
  • the controller 30 can control the bypass valve 36 to a partially open position so that a portion of the vapor refrigerant 42 flows through heat rejection heat-exchanger 20 and a remaining portion flows through bypass circuit 16. Further, the controller 30 can, in some embodiments, control the heat rejection heat-exchanger fan 26 to an off state to prevent any active heat exchange between the refrigerant and ambient air in the heat rejection heat-exchanger 20. Also, it has to be noted that, under some circumstances, such as excessive refrigerant charge migration at some environmental conditions, the controller 30 may control the bypass valve 36 to a closed position.
  • the high pressure and temperature refrigerant 42A exits the bypass refrigerant circuit 16 and/or the heat rejection heat-exchanger 20 and flows to the first reheat valve 34-1.
  • the controller 30 controls the first reheat valve 34- 1 to the open position so that the high pressure and temperature refrigerant 42A flows through the reheat coil 32, through the second reheat valve 34-2, and only then into the expansion device 22.
  • the second reheat valve 34-2 can be a check valve that allows the refrigerant 42B to exit the reheat refrigerant circuit 14 back into the cooling refrigerant circuit 12.
  • the second reheat valve 34-2 can be in electrical communication with the controller 30, which controls the second reheat valve 34-2 to the open position during the defrost mode of operation to allow the refrigerant 42B to reenter cooling refrigerant circuit 12.
  • the present disclosure has determined that the heat of the refrigerant 42A (supplemented by the heat provided by the evaporator fan 28) can be used to defrost the evaporator 24 in the manner discussed in more detail below by simply reversing the direction of flow of the indoor air 50 across the evaporator 24 from first direction 54 (FIGS. 1 and 2) to second direction 60 (FIG. 3).
  • the reheat coil 32 acts as a heat rejecting heat-exchanger where the heat is transferred from the refrigerant 42A to the indoor air 50 that is forced across the reheat coil 32 by the evaporator fan 28.
  • the indoor air 50 can be heated to a desired temperature so that the heated indoor air 62 can melt any frost that has formed on the outside surfaces of the evaporator 24.
  • the reheat coil 32 acts as a heat rejection heat-exchanger where during heat transfer interaction with the indoor air 50 so that the vapor refrigerant 42A is desuperheated to the point where it condenses to liquid refrigerant 42B that is then typically subcooled, in the case of a condenser, and is simply cooled to the thermodynamic state 42B, in the case of a gas cooler.
  • the expansion device 22 expands refrigerant 42B into a low pressure, low temperature two-phase mixture refrigerant 48 and flows it into the evaporator 24.
  • the evaporator 24 acts as a heat accepting heat-exchanger where heat transfer interaction is taking place between the refrigerant 48 and heated indoor air 62 that is forced across the evaporator 24 by the evaporator fan 28. In this manner, the refrigerant 48 is evaporated back into a low pressure vapor refrigerant 40, while the heated indoor air 62 is cooled to provide the air 64. The vapor refrigerant 40 then flows from the evaporator 24 back to the compressor 18.
  • the controller 30 activates the compressor 18, deactivates, when necessary, the heat rejection heat-exchanger fan 26, opens, if desired, the bypass valve 36, opens the first reheat valve 34-1 , controls, if necessary, the expansion valve 22, and causes the evaporator fan 28 to force the indoor air 50 across the evaporator 24 and the reheat coil 32 in the second direction 60.
  • the refrigerant system 10 can force the indoor air 50 in the second direction 60 by controlling the evaporator fan 28 to rotate in a second rotational direction 66, which is opposite the first rotational direction 56.
  • the refrigerant system 10 is described above by way of example providing the indoor air 50 in the first and second directions 54, 60 by changing the rotational direction of the evaporator fan 28 between the first and second rotational directions 56, 66.
  • the refrigerant system 10 it is contemplated by the present disclosure for the refrigerant system 10 to be configured in any manner to provide the indoor air 50 in the first and second directions 54, 60. It has to be understood that when the controller 30 operates the refrigerant system 10 in the defrost mode and moves the indoor air 50 in the second direction 60, the air 64 exiting the evaporator 24 may be directed either outdoors, indoors or to any other specified location.
  • FIGS. 4 and 5 an alternate embodiment of a configuration of the refrigerant system 10 that provides the indoor air 50 in the first and second directions 54, 60 is shown in FIGS. 4 and 5.
  • FIGS. 4 and 5 an alternate embodiment of a configuration of the refrigerant system 10 that provides the indoor air 50 in the first and second directions 54, 60 is shown in FIGS. 4 and 5.
  • FIGS. 4 and 5 only portions of the refrigerant system 10 are shown for purposes of clarity but air duct configuration is depicted in more detail.
  • the controller 30 controls the evaporator fan 28 to rotate in a single direction, such as the first rotational direction 56. Further, the controller 30 controls the position of one or more dampers 70 to change the direction of the flow of indoor air 50 through the indoor components of the refrigerant system 10.
  • dampers 70 are positioned so that when the refrigerant system 10 is in the normal mode of operation or the reheat mode of operation shown in FIG. 4, the indoor air 50 can be forced in the first direction 54 to result in the indoor air 50 being forced first across the evaporator 24 to form a conditioned air 52, which is then forced across the reheat coil 32.
  • the conditioned air 52 is not reheated by the reheat coil 32, which is disengaged, so that the cooled and typically dehumidified air 52 is provided to the conditioned environment in the manner discussed above.
  • the reheat mode of operation the conditioned air 52 is reheated by the reheat coil 32 so that reheated air 58 is provided to the conditioned environment in the manner discussed above.
  • the dampers 70 are positioned so that when the refrigerant system 10 is in the defrost mode of operation shown in FIG. 5, the indoor air 50 can be forced in the second direction 60 to result in the indoor air 50 being forced first across the reheat coil 32 to form the heated indoor air 62, which is then forced across the evaporator 24 to defrost the evaporator.
  • the refrigerant system 10 is illustrated by way of example in FIGS. 4 and 5 reversing the direction of airflow through the use of four dampers 70.
  • the refrigerant system 10 and associated air duct system including dampers 70 to have various configurations and additional design features. All these configurations are within the scope and can equally benefit from the disclosure.
  • FIGS. 1 through 3 may have various options and enhancement features, all of which are contemplated within the scope of and can equally benefit from the present disclosure.
  • the reheat refrigerant circuit 14 is illustrated in selective fluid communication with the cooling refrigerant circuit 12 at a location between the heat rejection heat-exchanger 20 and the expansion device 22.
  • the refrigerant system 10 it is contemplated by the present disclosure for the refrigerant system 10 to have any configuration of the reheat circuit 14 provided that the reheat coil 32 is positioned downstream with respect to the flow of indoor air 50 induced by the evaporator fan 28 during the normal and reheat modes of operation.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

L'invention concerne un système réfrigérant qui comprend un circuit de fluide frigorigène de refroidissement, un circuit de fluide frigorigène de réchauffement, un ventilateur d'évaporateur, et une unité de commande. Le ventilateur d'évaporateur contraint de l'air intérieur dans une première direction et une deuxième direction. L'air intérieur passe sur toute la surface de l'évaporateur avant le serpentin réchauffeur, dans la première direction, mais passe sur toute la surface du serpentin réchauffeur avant l'évaporateur, dans la deuxième direction. Lorsqu'elle est en mode de refroidissement classique, l'unité de commande commande le circuit de fluide frigorigène de réchauffement de sorte que ce dernier ne soit pas en communication fluidique avec le circuit de fluide frigorigène de refroidissement et commande le ventilateur d'évaporateur pour contraindre l'air intérieur dans la première direction. Lorsqu'elle est en mode de dégivrage, l'unité de commande commande le circuit de fluide frigorigène de réchauffement de sorte que ce dernier soit en communication fluidique avec le circuit de fluide frigorigène de refroidissement et commande le ventilateur d'évaporateur pour contraindre l'air intérieur dans la deuxième direction.
PCT/US2008/001225 2008-01-30 2008-01-30 Système réfrigérant à circuit de fluide frigorigène de réchauffement WO2009096915A1 (fr)

Priority Applications (4)

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PCT/US2008/001225 WO2009096915A1 (fr) 2008-01-30 2008-01-30 Système réfrigérant à circuit de fluide frigorigène de réchauffement
US12/864,122 US20100307172A1 (en) 2008-01-30 2008-01-30 Refrigerant system with reheat refrigerant circuit
CN2008801259834A CN101932883A (zh) 2008-01-30 2008-01-30 具有再热制冷剂回路的制冷剂系统
EP08724970A EP2250445A1 (fr) 2008-01-30 2008-01-30 Système réfrigérant à circuit de fluide frigorigène de réchauffement

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CN101932883A (zh) 2010-12-29
US20100307172A1 (en) 2010-12-09

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