WO2012112802A2 - Système de pompe à chaleur doté d'un système dirigeant le flux - Google Patents

Système de pompe à chaleur doté d'un système dirigeant le flux Download PDF

Info

Publication number
WO2012112802A2
WO2012112802A2 PCT/US2012/025496 US2012025496W WO2012112802A2 WO 2012112802 A2 WO2012112802 A2 WO 2012112802A2 US 2012025496 W US2012025496 W US 2012025496W WO 2012112802 A2 WO2012112802 A2 WO 2012112802A2
Authority
WO
WIPO (PCT)
Prior art keywords
manifold
refrigerant
heat exchanger
section
pump system
Prior art date
Application number
PCT/US2012/025496
Other languages
English (en)
Other versions
WO2012112802A3 (fr
Inventor
Jerome Anthony MATTER, III
Jeffrey Lee Tucker
Original Assignee
Johnson Controls Technology Company
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 Johnson Controls Technology Company filed Critical Johnson Controls Technology Company
Priority to CN201280009372.XA priority Critical patent/CN103380335B/zh
Publication of WO2012112802A2 publication Critical patent/WO2012112802A2/fr
Priority to US13/967,604 priority patent/US9752803B2/en
Publication of WO2012112802A3 publication Critical patent/WO2012112802A3/fr

Links

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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B39/00—Evaporators; Condensers
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/38—Expansion means; Dispositions thereof specially adapted for reversible cycles, e.g. bidirectional expansion restrictors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves

Definitions

  • the invention relates generally to the field of heating, ventilating, air conditioning, and refrigeration (HVAC&R) systems, and more particularly to heat pump systems with a flow directing system that allows a heat exchanger to be switchable between a single-pass arrangement and a two-pass arrangement.
  • HVAC&R heating, ventilating, air conditioning, and refrigeration
  • HVAC&R heating, ventilating, air conditioning and refrigeration
  • residential, light commercial, commercial and industrial systems are used to control temperatures and air quality in residences and buildings.
  • these systems operate by implementing a thermal cycle in which fluids are heated and cooled to provide the desired temperature in a controlled space, typically the inside of a residence or building.
  • Similar systems are used for vehicle cooling, and as well as for general refrigeration.
  • Controlled fluids within such systems are typically confined with enclosed circuits and include various refrigerants.
  • Refrigerants are specifically formulated to undergo phase changes within the normal operating temperatures and pressures of the systems so that considerable quantities of heat can be exchanged by virtue of the latent heat of vaporization of the circulated refrigerant.
  • the refrigerant is evaporated in one heat exchanger to draw heat from air circulating through the heat exchanger for cooling purposes.
  • the refrigerant is then condensed in a different heat exchanger to release heat from the refrigerant and thereby heat an air stream.
  • the system will function to heat or cool the air within the space.
  • the direction of refrigerant flow through evaporating and condensing heat exchangers can be reversed to allow for extraction of heat from a controlled space (cooling mode) and for the injection of heat into the space (heating mode).
  • vapor phase refrigerant may flow in a first direction from a compressor to an outdoor heat exchanger that condenses the refrigerant.
  • the liquid refrigerant may then flow through an expansion device to an indoor heat exchanger that evaporates the refrigerant to cool the controlled space.
  • the outdoor heat exchanger operates as a condenser and the indoor heat exchanger operates as an evaporator.
  • refrigerant flows through the system in an opposite direction, and the roles of the heat exchangers are reversed.
  • vapor phase refrigerant may flow from the compressor to the indoor heat exchanger, which condenses the refrigerant to heat the controlled space.
  • the refrigerant may then flow through the expansion valve to the outdoor heat exchanger, which evaporates the refrigerant.
  • the refrigerant then flows to the compressor to repeat the cycle through the system.
  • the outdoor heat exchanger operates as an evaporator and the indoor heat exchanger operates as a condenser.
  • the present invention relates to a heat pump system that includes a reversing valve configured to circulate a refrigerant through a closed loop in a first direction when the heat pump system is operating in a heating mode and in a second direction opposite of the first direction when the heat pump system is operating in a cooling mode.
  • the heat pump system also includes a compressor configured to compress the refrigerant, an indoor heat exchanger operable as a condenser in the heating mode and as an evaporator in the cooling mode, and an outdoor heat exchanger operable as a two-pass condenser in the cooling mode and as a single-pass evaporator in the heating mode.
  • the outdoor heat exchanger includes a first manifold, a second manifold subdivided by a baffle into a first section and a second section, and a plurality of tubes in fluid communication with the first manifold and the second manifold.
  • the heat pump system also includes a flow directing system and at least one expansion device disposed in the closed loop between the indoor heat exchanger and the outdoor heat exchanger, and configured to reduce pressure of the refrigerant.
  • the flow directing system includes one or more valves and piping segments of the closed loop and is configured to direct the refrigerant into the first section of the second manifold and out of the second section of the second manifold to the expansion device in the cooling mode and to direct the refrigerant into the first manifold and out of the first and second sections of the second manifold to the reversing valve in the heating mode.
  • the present invention also relates to a heat pump system that includes a reversing valve configured to circulate a refrigerant through a closed loop in a first direction when the heat pump system is operating in a heating mode and in a second direction opposite of the first direction when the heat pump system is operating in a cooling mode.
  • the heat pump system also includes a compressor configured to compress the refrigerant, an indoor heat exchanger operable as a condenser in the heating mode and as an evaporator in the cooling mode, and an outdoor heat exchanger operable as a two-pass condenser in the cooling mode and as a single-pass evaporator in the heating mode.
  • the outdoor heat exchanger includes a first manifold, a second manifold subdivided by a baffle into a first section and a second section, and a plurality of tubes in fluid communication with the first manifold and the second manifold.
  • the heat pump system also includes a flow directing system and at least one expansion device disposed in the closed loop between the indoor heat exchanger and the outdoor heat exchanger, and configured to reduce pressure of the refrigerant.
  • the flow directing system includes one or more valves and piping segments of the closed loop and is configured to direct the refrigerant into the first section of the second manifold and out of the second section of the second manifold to the expansion device in the cooling mode and to direct the refrigerant into the first section and second section of the second manifold and out of the first manifold to the reversing valve in the heating mode.
  • the present invention also relates to a heat pump system that includes a reversing valve configured to circulate a refrigerant through a closed loop in a first direction when the heat pump system is operating in a heating mode and in a second direction opposite of the first direction when the heat pump system is operating in a cooling mode.
  • the heat pump system also includes an indoor heat exchanger, an outdoor heat exchanger, and a flow directing system.
  • the outdoor heat exchanger includes a first manifold, a second manifold subdivided by a baffle into a first section and a second section, and a plurality of tubes in fluid communication with the first manifold and the second manifold.
  • the flow directing system includes one or more valves and piping segments of the closed loop and is configured to, in the cooling mode, direct the refrigerant to enter the outdoor heat exchanger through the first section of the second manifold and to exit the outdoor heat exchanger through the second section of the second manifold and, in the heating mode, to direct the refrigerant to enter the outdoor heat exchanger through the first manifold and to exit the outdoor heat exchanger through the first and second sections of the second manifold or to direct the refrigerant to enter the outdoor heat exchanger through the first and second sections of the second manifold and to exit the outdoor heat exchanger through the first manifold.
  • FIGURE 1 is an illustration of an embodiment of a residential HVAC&R system that may employ a heat pump system with an outdoor heat exchanger switchable between a two-pass condenser and a single -pass evaporator, in accordance with the present techniques.
  • FIGURE 2 is a diagrammatical overview showing the cooling mode of the heat pump system of FIGURE 1, in accordance with the present techniques.
  • FIGURE 3 is a diagrammatical overview showing the heating mode of the heat pump system of FIGURE 2, in accordance with the present techniques.
  • FIGURE 4 is a diagrammatical overview showing the cooling mode of another embodiment of a heat pump system with outdoor and indoor heat exchangers switchable between two-pass condensers and single-pass evaporator, in accordance with the present techniques.
  • FIGURE 5 is a diagrammatical overview showing the heating mode of the heat pump system of FIGURE 4, in accordance with the present techniques.
  • FIGURE 6 is a diagrammatical overview showing the cooling mode of another embodiment of a heat pump system with outdoor and indoor heat exchangers switchable between two-pass condensers and single-pass evaporator, in accordance with the present techniques.
  • FIGURE 7 is a diagrammatical overview showing the heating mode of the heat pump system of FIGURE 6, in accordance with the present techniques.
  • the present application is directed to heat pump systems that include an outdoor heat exchanger that is switchable between a single-pass arrangement and a two-pass arrangement.
  • the outdoor heat exchanger is designed to function as a two-pass condenser when the heat pump system is operating in a cooling mode and as a single-pass evaporator when the heat pump system is operating in a heating mode.
  • the operation of the outdoor heat exchanger as a two-pass condenser may promote subcooling of the refrigerant in the cooling mode, which in turn, may improve the operating efficiency of the heat pump system.
  • the operation of the outdoor heat exchanger as a single -pass evaporator may allow the liquid refrigerant entering the evaporator to be distributed to each of the heat exchanger tubes to promote efficient evaporation of the liquid refrigerant within the heat exchanger tubes with a low pressure drop, which can enhance system performance.
  • a flow directing system of check valves and piping segments enables switching of the outdoor heat exchanger between the single-pass arrangement and the two-pass arrangement.
  • the check valves are disposed in the closed loop external to the outdoor heat exchanger to facilitate maintenance.
  • the outdoor heat exchanger generally includes at least two sets of heat exchange tubes designed to direct refrigerant between two manifolds of the heat exchanger.
  • the piping segments and check valves are designed to direct fluid into one manifold in the cooling mode and into the other manifold in the heating mode. For example, in the cooling mode, refrigerant enters the outdoor heat exchanger through a first manifold, flows through one set of tubes to the second manifold, and returns to the first manifold through a second set of tubes. In the heating mode, refrigerant enters the outdoor heat exchanger through the second manifold and flows through both sets of tubes in parallel to the first manifold.
  • FIGURE 1 depicts an exemplary application for a heat pump system that employs an outdoor heat exchanger that is switchable between a two-pass arrangement and a single-pass arrangement.
  • Such systems in general, may be applied in a range of settings, both within the HVAC&R field and outside of that field.
  • heat pump systems may be used in residential, commercial, light industrial, industrial and in any other application for heating and cooling a volume or enclosure, such as a residence, building, structure, and so forth.
  • a heat pump system 10 can be employed in a building, such as a residence 12.
  • Heat pump system 10 includes a closed loop 14 that circulates a fluid, such as refrigerant, between an indoor unit 16 and an outdoor unit 18.
  • Indoor unit 16 may be positioned in a utility room, an attic, a basement, and so forth.
  • Outdoor unit 18 is typically situated adjacent to a side of residence 12 and is covered by a shroud to protect the system components and to prevent leaves and other contaminants from entering the unit.
  • Closed loop 14 includes piping that transfers refrigerant between indoor unit 16 and outdoor unit 18, typically transferring primarily liquid refrigerant in one direction and primarily vaporized refrigerant in an opposite direction.
  • a heat exchanger in outdoor unit 18 functions as a condenser for condensing vaporized refrigerant flowing from indoor unit 16 to outdoor unit 18 within closed loop 14.
  • a heat exchanger of indoor unit 16 functions as an evaporator for evaporating liquid refrigerant before returning the refrigerant to outdoor unit 18.
  • Outdoor unit 18 draws in environmental air through its sides as indicated by the arrows directed to the sides of the unit, forces the air through outdoor unit 18 by means of a fan (not shown), and expels the air as indicated by the arrows above outdoor unit 18.
  • a fan not shown
  • the air is heated by the heat exchanger of outdoor unit 18 and exits the top of the unit at a temperature higher than it entered the sides.
  • Air is blown over the heat exchanger of indoor unit 16 and is then circulated through residence 12 by means of ductwork 20, as indicated by the arrows entering and exiting ductwork 20.
  • the overall system operates to maintain a desired temperature as set by a thermostat 22.
  • FIGURES 2 and 3 depict the flow of refrigerant through heat pump system 10, with arrows used to depict the direction of refrigerant flow.
  • FIGURE 2 depicts heat pump system 10 operating in a cooling mode where the heat exchanger in the outdoor unit functions as a condenser and the heat exchanger in the indoor unit functions as an evaporator.
  • FIGURE 3 depicts the heat pump system operating in the heating mode where the heat exchanger in the indoor unit functions as a condenser and the heat exchanger in the outdoor unit functions as an evaporator.
  • the flow of refrigerant through heat pump system 10 is reversed when switching between the cooling and heating modes.
  • Refrigerant flows through heat pump system 10 within closed loop 14. Because heat pump system 10 can operate in both a cooling mode and a heating mode, refrigerant can flow through closed loop 14 in one direction for the cooling mode as shown in FIGURE 2, and in the opposite direction for the heating mode, as shown in FIGURE 3.
  • the refrigerant may be any fluid that absorbs and extracts heat.
  • the refrigerant may be hydro fluorocarbon (HFC) based R-410A, R-407, or R-134a, or it may be carbon dioxide (R-744) or ammonia (R-717).
  • Heat pump system 10 also includes an indoor heat exchanger 24, an outdoor heat exchanger 26, expansion devices 28 and 29, and a compressor 30.
  • Each heat exchanger 24 and 26 may function as an evaporator and a condenser, depending on the operational mode of the heat pump system. For example, when heat pump system 10 is operating in the cooling mode, outdoor heat exchanger 26 functions as a condenser, releasing heat to the outside air, while indoor heat exchanger 24 functions as an evaporator, absorbing heat from the inside air. When heat pump system 10 is operating in the heating mode, outdoor heat exchanger 26 functions as an evaporator, absorbing heat from the outside air, while indoor heat exchanger 24 functions as a condenser, releasing heat to the inside air.
  • FIGURE 2 depicts heat pump system 10 operating in the cooling mode. Accordingly, outdoor heat exchanger 26 operates as a two-pass condenser and indoor heat exchanger 24 functions as an evaporator. Heat pump system 10 cools an environment by circulating refrigerant within closed loop 14 through indoor heat exchanger 24, compressor 30, outdoor heat exchanger 26, and expansion devices 28 and 29.
  • compressor 30 Within closed loop 14, refrigerant flows to compressor 30 as primarily a low pressure and temperature vapor. Compressor 30 reduces the volume available for the refrigerant vapor, consequently, increasing the pressure and temperature of the vapor refrigerant.
  • Compressor 30 may be any suitable compressor such as a screw compressor, reciprocating compressor, rotary compressor, swing link compressor, scroll compressor, or turbine compressor.
  • Compressor 30 is driven by a motor 32 that receives power from a variable speed drive (VSD) or a direct AC or DC power source.
  • Motor 32 may receive fixed line voltage and frequency from an AC power source, a variable voltage, or frequency drive.
  • motor 32 may be a switched reluctance (SR) motor, an induction motor, an electronically commutated permanent magnet motor (ECM), or any other suitable motor type.
  • SR switched reluctance
  • ECM electronically commutated permanent magnet motor
  • reversing valve 34 is positioned in refrigeration circuit 14 between the outdoor and indoor heat exchangers 26 and 24 to control the direction of refrigerant flow through the closed loop 14 and to thereby switch the heat pump system 10 between the cooling mode and the heating mode.
  • reversing valve 34 includes a cooling position 36 that directs refrigerant through closed loop 14 in a first direction, as shown in FIGURE 2, when the heat pump system 10 is operating in the cooling mode.
  • Reversing valve 36 also includes a heating position 38 that directs refrigerant through closed loop 14 in an opposite direction, as shown in FIGURE 3, when the heat pump system 10 is operating in the heating mode.
  • a solenoid 40 can be actuated by signals from control circuitry 42 to switch reversing valve 34 between the cooling and heating position 36 and 38.
  • the refrigerant After flowing through reversing valve 34, the refrigerant enters outdoor heat exchanger 26 (operating as a condenser) through a manifold 44.
  • Manifold 44 is divided into sections 46 and 48 by a baffle 50.
  • baffle 50 may be inserted, affixed, and/or interference fit within manifold 44 to impede the flow of refrigerant between sections 46 and 48 of manifold 44.
  • baffle 50 may be an integral part of manifold 44 and/or may be a double baffle.
  • Baffle 50 separates refrigerant entering outdoor heat exchanger 26 from refrigerant exiting outdoor heat exchanger 26, creating two-passes for refrigerant flowing through the heat exchanger in the cooling mode.
  • baffle 50 directs refrigerant entering manifold 44 though section 46 into tubes 52.
  • the refrigerant then flows through tubes 52 into manifold 54.
  • the refrigerant may be cooled by air that is pushed or pulled across tubes 52, for example, by a fan.
  • some, or all, of the refrigerant may be condensed as the refrigerant flows through tubes 52 and transfers heat to the environment.
  • the refrigerant flows through tubes 56 to section 48 of manifold 44.
  • the refrigerant may be cooled by air that is drawn across tubes 56, for example, by a fan.
  • the refrigerant may be subcooled as the refrigerant flows through tubes 56.
  • the refrigerant flows through outdoor heat exchanger 26 in two passes.
  • the refrigerant is cooled as the refrigerant flows through tubes 52 from section 46 of manifold 44 to manifold 54.
  • the refrigerant then flows through tubes 56 from manifold 54 to the other section 48 of manifold 44 in a second pass.
  • manifold 54 may include a distributor device 58, which may be used to distribute the flow of refrigerant in the heating mode, as described below with respect to FIGURE 3.
  • distributor device 58 may be omitted or refrigerant distribution can be accomplished with a different device.
  • Fins 60 are located between tubes 52 and 56 to promote heat transfer between tubes 52 and 56 and the environment.
  • the fins are constructed of aluminum, brazed or otherwise jointed to the tubes, and disposed generally perpendicular to the flow of refrigerant.
  • the fins may be made of other materials that facilitate heat transfer and may extend parallel or at varying angles with respect to the flow of refrigerant.
  • the fins may be corrugated fins or plate fins and, in certain embodiments, may include features such as louvers, collars, and the like. Further, in certain embodiments, the fins may be omitted.
  • heat exchanger 26 has generally horizontal tubes 52 and 56 that extend between generally vertical manifolds 44 and 54.
  • the heat exchanger may be rotated approximately 90 degrees so that the tubes extend vertically between a top and bottom manifold.
  • the heat exchanger may be provided in a single plane or slab, or may include bends, corners, contours, and so forth.
  • the manifolds and tubes may be constructed of aluminum or any other material that promotes good heat transfer.
  • the tubes may be multichannel tubes that each contain two or more generally parallel flow paths extending along the length of the tubes.
  • the tubes may be generally round tubes that each contain a single flow path.
  • Piping segment 62 is part of a flow directing system 67 that is included within closed loop 14.
  • Flow directing system 67 includes piping segment 62, as well as a check valve 68 disposed in piping segment 62, piping segments 70 and 72, and check valves 74 and 76 that are disposed in piping segments 70 and 72, respectively.
  • Flow directing system 67 is designed to direct the flow of refrigerant through outdoor heat exchanger 26 in a two-pass arrangement in the cooling mode and in a single-pass arrangement in the heating mode.
  • flow directing system 67 directs refrigerant into outdoor heat exchanger 26 though section 46 of manifold 44 and out of outdoor heat exchanger 26 through section 48 of manifold 44. Accordingly, refrigerant enters and exits outdoor heat exchanger 26 through different sections of the same manifold, allowing refrigerant to flow through the heat exchanger in a two-pass arrangement. The refrigerant exiting outdoor heat exchanger 26 then flows through piping segment 62 and check valve 68 to expansion devices 28 and 29.
  • Check valves 68, 74, and 76 are designed to control the direction of refrigerant flow through closed loop 14.
  • Check valves 68, 74, and 76 may be ball check valves, diaphragm check valves, swing check valves, or other types of check valve suitable for unidirectional flow.
  • check valves 68, 74, and 76 direct flow from section 48 of manifold 44 through piping segment 62 to expansion devices 28 and 29.
  • check valve 68 allows flow from manifold 44 through piping segment 62 while check valves 74 and 76 inhibit the flow of refrigerant from piping segment 62 through piping segments 70 and 74, respectively, thereby directing the refrigerant to expansion devices 28 and 29.
  • refrigerant flows through piping segment 62 of closed loop 14 and bypasses segments 70 and 72 of closed loop 14.
  • check valves 68, 74, and 76 direct flow from expansion devices 28 and 29 through piping segment 70 into manifold 54 of outdoor heat exchanger 26.
  • the check valves 68, 74, and 76 also direct flow from section 48 of manifold 44 through piping segment 72 to reversing valve 34. Accordingly, in the heating mode, refrigerant flows through piping segments 70 and 72 and bypasses piping segment 62.
  • heat pump system 10 includes two unidirectional expansion devices 28 and 29, with one expansion device 28 being employed to expand the refrigerant in the cooling mode and the other expansion device 29 being employed to expand the refrigerant in the heating mode.
  • a single bi-directional expansion device may be employed.
  • expansion devices 28 and 29 are thermal expansion valves (TXV); however, in other embodiments, expansion devices 28 and 29 may be orifices, capillary tubes, or any combination of such devices.
  • TXV thermal expansion valves
  • expansion devices 28 and 29 may be orifices, capillary tubes, or any combination of such devices.
  • the refrigerant exits expansion devices 28 and 29 as a two-phase refrigerant.
  • the refrigerant flows to indoor heat exchanger 24 (operating as an evaporator).
  • Refrigerant enters indoor heat exchanger 24 through a connection 78 and then flows through indoor heat exchanger 24 to exit through a connection 80.
  • the refrigerant may be heated to evaporate the refrigerant.
  • the refrigerant may be heated by a fluid, such as air or water, that is directed over the tubes.
  • Indoor heat exchanger 24 may be any suitable type of heat exchanger, such as a fin and tube heat exchanger, a shell and tube heat exchanger, a plate heat exchanger, a multichannel heat exchanger, or a chiller, among others.
  • the refrigerant exits indoor heat exchanger 24 through connection 80 and flows through reversing valve 34 to compressor 30 as primarily a low pressure and low temperature vapor. Within compressor 30, the refrigerant is compressed to primarily a high temperature and high pressure vapor that is ready to enter outdoor heat exchanger 26 and begin the refrigeration cycle again.
  • control circuitry 42 which receives inputs from sensors 84, 86, and 88 and thermostat 22.
  • control circuitry 42 may use information received from thermostat 22 to switch heat pump system 10 between the heating mode and the cooling mode. For example, if the thermostat 22 is set to a cooling mode, control circuitry 42 will send a signal to solenoid 40 to place reversing valve 34 in cooling position 36, as shown in FIGURE 2. In another example, if the thermostat 22 is set to a heating mode, control circuitry 42 will send a signal to solenoid 40 to place reversing valve 34 in heating position 38, as shown in FIGURE 3.
  • Control circuitry 42 may execute hardware or software control algorithms to regulate heat pump system 10.
  • control circuitry 42 may include an analog to digital (A/D) converter, a microprocessor, a non-volatile memory, and an interface board.
  • A/D analog to digital
  • Sensors 84, 86, and 88 also can provide inputs to control circuitry 42.
  • sensor 84 detects the ambient air temperature and provides the temperature to control circuitry 42.
  • Control circuitry 42 then compares the temperature received from sensor 84 to the temperature set point received from the thermostat 22. If the temperature is above the temperature set point in the cooling mode, or below the temperature set point in the heating mode, control circuitry 42 may turn on compressor motor 32, as well as fans for heat exchangers 24 and 26, to run heat pump system 10.
  • Input from sensors 86 and 88 may be employed to initiate a defrost cycle when the heat pump system 10 is operating in the heating mode. For example, when the outdoor temperature approaches freezing, moisture in the outside air that is directed over outdoor heat exchanger 26 may condense and freeze on the coil. Sensor 86 measures the outside air temperature, and sensor 88 measures the temperature of outdoor heat exchanger tubes 52 and/or 56. According to certain embodiments, if either sensor 86 or 88 provides a temperature below freezing to control circuitry 42, heat pump system 10 may be placed in a defrost mode where solenoid 40 is actuated to place reversing valve 34 in the cooling position 36 and the fan for the outdoor heat exchanger 26 is turned off.
  • Heat pump system 10 may operate in the cooling mode until the increased temperature and pressure refrigerant flowing through tubes 52 and 56 defrosts the tubes. Once sensor 88 detects that the tubes have defrosted, control circuitry 42 returns the reversing valve 34 to the heating position 38. As may be appreciated, the defrost cycle can be set to occur at many different time and temperature conditions. Further, other devices may be included in heat pump system 10, such as additional pressure and/or temperature transducers or switches that sense temperatures and pressures of the refrigerant, the heat exchangers, the inlet and outlet air, and so forth.
  • FIGURE 3 depicts heat pump system 10 operating in the heating mode where indoor heat exchanger 24 functions as a condenser and outdoor heat exchanger 26 functions as a single-pass evaporator.
  • reversing valve 34 is in the heating position 38 and the flow of refrigerant through closed loop 14 is reversed.
  • the flow directing system 67 allows refrigerant to flow through outdoor heat exchanger 26 in a single-pass arrangement.
  • compressor 30 compresses vapor refrigerant to a primarily high temperature and high pressure vapor.
  • the refrigerant flows through reversing valve 34 to indoor heat exchanger 24, which operates as a condenser.
  • the refrigerant enters indoor heat exchanger 24 through connection 80 and then flows heat exchanger 24 to exit through connection 78.
  • the refrigerant may flow through heat exchanger 24 in the opposite direction from the cooling mode.
  • connection 80 functions as an inlet
  • connection 78 functions as the inlet.
  • the refrigerant may be cooled by fluid, such as water or air, that is drawn across tubes of the heat exchanger to condense the refrigerant.
  • the refrigerant then flows through expansion devices 28 and 29.
  • the refrigerant is expanded in expansion device 29 to become primarily a low pressure and low temperature two-phase refrigerant, while expansion device 28 is generally inactive.
  • a single bi-directional expansion device may be employed rather than two unidirectional expansion devices.
  • the refrigerant flows through connection point 66, piping segment 70, and check valve 74 to manifold 54 of outdoor heat exchanger 26.
  • Check valve 68 inhibits the flow of refrigerant through piping segment 62, thereby directing the refrigerant through piping segment 70 to manifold 54.
  • the refrigerant enters outdoor heat exchanger 26 through the opposite manifold that is used in the cooling mode.
  • the refrigerant enters outdoor heat exchanger 26 through manifold 54, while in the cooling mode, the refrigerant enters outdoor heat exchanger 26 through manifold 44.
  • distributor device 58 which distributes the liquid refrigerant along the length of the manifold.
  • distributor device 58 may be a circular tube or pipe concentrically disposed inside manifold 54.
  • distributor device 58 may have a rectangular, trapezoidal, elliptical, or triangular cross-section, among others, and/or may be disposed off-center within manifold 54.
  • Distributor device 58 may include a series of apertures disposed along the length of the distributor device to meter refrigerant flowing through the interior of the distributor device into the manifold.
  • distributor device 58 may include a series of apertures, with each aperture corresponding to one of the tubes 52 or 56. However, in other embodiments, the number and/or alignment of the apertures may vary. Further, in certain embodiments, distributor device 58 may be omitted and refrigerant may be supplied directly into manifold 54. Moreover, in other embodiments, a different type of distributor may be used. [0046] From manifold 54, the refrigerant flows through both sets of tubes 52 and 56 to manifold 44. In particular, the refrigerant flows through tubes 52 to section 46 of manifold 44 and through tubes 56 to section 48 of manifold 44.
  • refrigerant flows through outdoor heat exchanger 26 in a single-pass arrangement where refrigerant flows through each set of tubes 52 and 56 in parallel.
  • the refrigerant flows through tubes 52 and 56, the refrigerant is heated by air that is drawn across tubes 52 and 56.
  • some, or all, of the refrigerant is evaporated as the refrigerant flows through tubes 52 and 56 and absorbs heat from the environment.
  • the refrigerant from each section 46 and 48 of manifold 44 exits manifold 44 through separate outlets and is directed to reversing valve 34.
  • the refrigerant from section 46 flows through connection point 90 and into reversing valve 34.
  • the refrigerant from section 48 flows through connection point 64, through piping segment 72, through check valve 76, and through connection point 90 into reversing valve 34.
  • piping segment 72 allows refrigerant from section 48 of manifold 44 to be recombined with the refrigerant from section 46 of manifold 44 and directed into reversing valve 34.
  • flow directing system 67 directs refrigerant through outdoor heat exchanger 26 in a single-pass.
  • Refrigerant enters outdoor heat exchanger 26 through manifold 54, flows through tubes 52 and 56, and exits heat exchanger 26 through manifold 44.
  • Piping segment 70 directs refrigerant into manifold 54 of heat exchanger 26 and piping segment 72 allows refrigerant exiting section 48 of manifold 44 to be combined with the refrigerant exiting section 46 of manifold 44. Accordingly, in the heating mode, refrigerant flows through piping segments 70 and 72 and bypasses segments 67.
  • the refrigerant from the different sections 46 and 48 of manifold 44 is rejoined upstream of reversing valve 34 at connection point 90.
  • the refrigerant from the different sections 46 and 48 may be rejoined within the reversing valve.
  • the refrigerant flows through compressor 30 where the refrigerant is compressed to primarily a high temperature and high pressure vapor.
  • the refrigerant is then directed to the indoor heat exchanger 24 to begin the refrigeration cycle again.
  • FIGURES 4 and 5 depict another embodiment of a heat pump system 91. Similar to heat pump system 10 (FIGURES 2 and 3), heat pump system 91 includes flow directing system 67, which allows outdoor heat exchanger 26 to operate as a two-pass condenser in the cooling mode and as a single-pass evaporator in the heating mode. Further, heat pump system 91 includes a flow directing system 92 that allows an indoor heat exchanger 93 to switch between a two-pass and a single-pass arrangement.
  • flow directing system 92 includes piping segments 94, 96, and 98 and check valves 100, 102, and 104 that allow indoor heat exchanger 93 to function as a single-pass evaporator when operating in the cooling mode shown in FIGURE 4 and as a two-pass condenser when operating in the heating mode shown in FIGURE 5.
  • Check valves 100, 102, and 104 are designed to control the direction of refrigerant flow through closed loop 14.
  • Check valves 100, 102, and 104 may be ball check valves, diaphragm check valves, swing check valves, or other types of check valve suitable for unidirectional flow.
  • Indoor heat exchanger 93 includes manifolds 106 and 108 that are connected by tubes 110 and 112.
  • the manifolds and tubes may be constructed of aluminum or any other material that promotes good heat transfer.
  • the tubes may be multichannel tubes that each contain two or more generally parallel flow paths extending along the length of the tubes.
  • the tubes may be generally round tubes that each contain a single flow path.
  • Fins 113 are located between tubes 110 and 112 to promote heat transfer between tubes 110 and 112 and the environment.
  • the fins are constructed of aluminum, brazed or otherwise jointed to the tubes, and disposed generally perpendicular to the flow of refrigerant.
  • the fins may be made of other materials that facilitate heat transfer and may extend parallel or at varying angles with respect to the flow of refrigerant.
  • the fins may be corrugated fins or plate fins and, in certain embodiments, may include features such as louvers, collars, and the like. Further, in certain embodiments, the fins may be omitted.
  • Manifold 108 is divided into sections 114 and 116 by a baffle 118.
  • baffle 118 may be inserted, affixed, and/or interference fit within manifold 108 to impede the flow of refrigerant between sections 114 and 116 of manifold 108.
  • baffle 118 may be an integral part of manifold 108 and/or may be a double baffle. In the heating mode, discussed below with respect to FIGURE 5, baffle 118 separates refrigerant entering indoor heat exchanger 93 from refrigerant exiting indoor heat exchanger 93, creating two-passes for refrigerant flowing through the heat exchanger in the heating mode.
  • manifold 106 may include a distributor device 120, which may be used to distribute the flow of refrigerant in the cooling mode, as described below with respect to FIGURE 4.
  • distributor device 120 may be a circular tube or pipe concentrically disposed inside manifold 106.
  • distributor device 120 may have a rectangular, trapezoidal, elliptical, or triangular cross-section, among others, and/or may be disposed off-center within manifold 106.
  • Distributor device 120 may include a series of apertures disposed along the length of the distributor device to meter refrigerant flowing through the interior of the distributor device into the manifold.
  • distributor device 120 may include a series of apertures, with each aperture corresponding to one of the tubes 110 or 112. However, in other embodiments, the number and/or alignment of the apertures may vary. Further, in certain embodiments, distributor device 120 may be omitted and refrigerant may be supplied directly into manifold 106. Moreover, in other embodiments, a different type of distributor may be used.
  • FIGURE 4 depicts heat pump system 91 operating in the cooling mode where outdoor heat exchanger 26 functions as a two-pass condenser and indoor heat exchanger 93 functions as a single-pass evaporator.
  • Refrigerant is compressed in compressor 30 and flows through reversing valve 34, connection point 90, outdoor heat exchanger 26, piping segment 62, check valve 68, connection point 60, and expansion devices 28 and 29, as described previously in relation to FIGURE 2.
  • the refrigerant then flows through connection point 122, which connects piping segments 94 and 98.
  • check valves 100 and 104 direct flow from expansion devices 28 and 29 through piping segment 94 into manifold 106 of outdoor heat exchanger 93.
  • check valve 100 allows flow from connection point 122 through piping segment 94, while check valves 104 inhibits the flow of refrigerant from connection point 122 through piping segment 98. Accordingly, in the cooling mode, refrigerant flows through piping segment 94 of closed loop 14 and bypasses segment 98 of closed loop 14.
  • the refrigerant from piping segment 94 flows into distributor device 120, which distributes the liquid refrigerant along the length of the manifold. From manifold 106, the refrigerant flows through both sets of tubes 110 and 112 to sections 114 and 116 of manifold 108, respectively. Accordingly, in the cooling mode, refrigerant flows through indoor heat exchanger 93 in a single-pass arrangement where refrigerant flows through each set of tubes 110 and 112 in parallel. As the refrigerant flows through tubes 110 and 112, the refrigerant is heated by a fluid, such as air, that is drawn across tubes 110 and 112. According to certain embodiments, some, or all, of the refrigerant is evaporated as the refrigerant flows through tubes 110 and 112 and absorbs heat from the environment.
  • a fluid such as air
  • the refrigerant from each section 114 and 116 of manifold 108 exits manifold 108 through separate outlets and is directed to reversing valve 34.
  • the refrigerant from section 114 flows through connection point 126 and into reversing valve 34.
  • Check valve 102 inhibits the flow of refrigerant from connection point 126 into piping segment 96, and accordingly directs the refrigerant exiting section 114 to reversing valve 34.
  • the refrigerant from section 116 flows through connection point 124, through piping segment 96, through check valve 102, and through connection point 126 into reversing valve 34. Accordingly, piping segment 96 allows refrigerant from section 116 of manifold 108 to be recombined with the refrigerant from section 114 of manifold 108.
  • the refrigerant from the different sections 114 and 116 of manifold 108 is rejoined upstream of reversing valve 34 at connection point 126.
  • the refrigerant from the different sections 114 and 116 may be rejoined within the reversing valve.
  • the refrigerant flows to compressor 30 as primarily a low pressure and temperature vapor.
  • the refrigerant is compressed to primarily a high temperature and high pressure vapor that is ready to enter outdoor heat exchanger 26 and begin the refrigeration cycle again.
  • FIGURE 5 depicts heat pump system 91 operating in the heating mode where outdoor heat exchanger 26 functions as a single-pass evaporator and indoor heat exchanger 93 functions as a two-pass condenser. From compressor 30, the refrigerant flows through reversing valve 34 and connection point 126 to indoor heat exchanger 93. Check valve 102 inhibits the flow of refrigerant from connection point 126 into piping segment 96, and, consequently, piping segment 96 is bypassed in the heating mode.
  • the refrigerant enters indoor heat exchanger 93 through section 114 of manifold 108.
  • Baffle 118 separates refrigerant entering indoor heat exchanger 93 from refrigerant exiting indoor heat exchanger 93, creating two-passes for refrigerant flowing through the heat exchanger in the heating mode.
  • baffle 118 directs refrigerant entering manifold 108 though section 114 into tubes 110.
  • the refrigerant then flows through tubes 110 into manifold 106. From manifold 106 refrigerant flows through tubes 112 to section 116 of manifold 108. As the refrigerant flows through tubes 110 and 112, the refrigerant may be condensed and/or subcooled as the refrigerant transfers heat to the environment.
  • the refrigerant flows through indoor heat exchanger 93 in two passes.
  • the refrigerant is cooled as the refrigerant flows through tubes 110 from section 114 of manifold 108 to manifold 106.
  • the refrigerant then flows through tubes 112 from manifold 106 to the other section 116 of manifold 108 in a second pass.
  • the refrigerant flows through each set of tubes 1 10 and 112 in series.
  • the refrigerant exits indoor heat exchanger 93 through section 116 of manifold 108 and flows through connection point 124 to piping segment 98.
  • the refrigerant then flows through piping segment 98, check valve 104, and connection point 122 to expansion devices 28 and 29.
  • the head pressure differential within the system 91 may inhibit the flow of refrigerant from connection point 124 towards connection point 126 and from connection point 122 into piping segment 94.
  • connection point 122 From connection point 122, the refrigerant flows through expansion devices 29 and 28, connection point 66, check valve 74, outdoor heat exchanger 26, piping segment 72, and check valve 76 to connection point 90, as described above with respect to FIGURE 3.
  • connection point 90 the refrigerant from sections 46 and 48 of manifold 44 is combined and directed through reversing valve 34 to compressor 30, where the refrigeration cycle may begin again.
  • FIGURES 6 and 7 depict another embodiment of a heat pump system 128. Similar to heat pump system 91 (FIGURES 4 and 5), heat pump system 128 includes an outdoor heat exchanger 129 and an indoor heat exchanger 130 that are switchable between a two-pass arrangement and a single-pass arrangement. However, rather than including flow directing systems 67 and 92 (FIGURES 4 and 5) that allow refrigerant to enter the heat exchangers through different inlet manifolds in the heating and cooling modes, heat pump system 128 includes flow directing systems 131 and 132 that allow refrigerant to exit the heat exchangers through different outlet manifolds in the heating and cooling modes.
  • flow 67 and 92 FIGURES 4 and 5
  • Flow directing system 131 includes a switching valve 134, a check valve 138, and piping segments 140, 142, 144, and 146 that allow outdoor heat exchanger 129 to be switched between a two-pass condenser where refrigerant enters and exits the heat exchanger through manifold 44 and a single-pass evaporator where refrigerant enters the heat exchanger through manifold 44 and exits the heat exchanger through manifold 54.
  • Flow directing system 132 includes a switching valve 136, a check valve 148, and piping segments 150, 152, 154, and 156 that allow indoor heat exchanger 130 to be switched between a single-pass evaporator where refrigerant enters the heat exchanger through manifold 106 and exits the heat exchanger through manifold 108 and a two-pass condenser where refrigerant enters and exits the heat exchanger through manifold 106.
  • Check valves 138 and 148 are designed to control the direction of refrigerant flow through closed loop 14.
  • Check valves 138 and 148 may be ball check valves, diaphragm check valves, swing check valves, or other types of check valve suitable for unidirectional flow.
  • Switching valves 134 and 136 can be electrically coupled to controller 42 and actuated by controller 42 when switching heat pump system 128 between the cooling mode and the heating mode. Further, switching valves 134 and 136 can be any suitable type of three-way control valves, such as pneumatic or solenoid valves among others.
  • Heat exchangers 129 and 130 are generally similar to heat exchangers 26 and 93, discussed above with respect to FIGURE 4. However, rather than including a single distributor device, each heat exchanger 129 and 130 includes a pair of distributor devices 158, 160, 162, and 164.
  • manifold 44 of outdoor heat exchanger 129 includes distributor device 158 disposed in section 46 and distributor device 160 disposed in section 48.
  • Manifold 106 of indoor heat exchanger 130 is divided into sections 166 and 168 by a baffle 170.
  • Distributor device 162 is disposed in section 166 and distributor device 164 is disposed in section 168.
  • distributor devices 158, 160, 162, and 164 can be employed to distribute refrigerant along the respective manifold sections 46, 48, 166, and 168 when the heat exchangers 129 and 130 are functioning as single-pass evaporators.
  • distributor devices 158, 160, 162, and 164 may be circular tubes or pipes concentrically disposed inside manifold 44 or 106.
  • distributor devices 158, 160, 162, and 164 may include a series of apertures disposed along the length of the distributor device to meter refrigerant flowing through the interior of the distributor device into the manifold.
  • FIGURE 6 depicts heat pump system 128 operating in the cooling mode with outdoor heat exchanger 129 operating as a two-pass condenser and indoor heat exchanger 130 operating as a single -pass evaporator. Refrigerant is compressed in compressor 30 and flows through reversing valve 34 to switching valve 134.
  • switching valve 134 is disposed in the cooling position 172 to direct refrigerant from switching valve 134 through piping segment 140 to manifold 44 of outdoor heat exchanger 129. Accordingly, in the cooling mode, the refrigerant bypasses piping segment 146.
  • the refrigerant flows into distributor device 158 within section 46 of manifold 44.
  • Distributor device 158 distributes the refrigerant along the length of section 46 and into tubes 52.
  • Piping segment 144 is also connected to distributor 158; however, check valve 138 inhibits flow from distributor device 158 into piping segment 138.
  • the refrigerant flows through tubes 52 into manifold 54.
  • the refrigerant then flows through tubes 56 to section 48 of manifold 44. Accordingly, in the cooling mode, the refrigerant flows through outdoor heat exchanger 129 in two passes where the refrigerant flows through each set of tubes 52 and 56 in series.
  • the refrigerant may be condensed and/or subcooled as the refrigerant transfers heat to the environment.
  • the refrigerant exits outdoor heat exchanger 129 through section 48 of manifold 44 and flows through a piping segment 142.
  • the refrigerant then flows through a connection point 174, which connects piping segments 142 and 144 to the rest of closed loop 14.
  • the pressure differential within the heat pump system 128 inhibits the flow of refrigerant from connection point 174 into piping segment 144, and directs the refrigerant from connection point 174 to expansion devices 28 and 29.
  • expansion device 28 Within expansion device 28, the refrigerant expands to become primarily a low pressure and low temperature two-phase refrigerant.
  • connection point 176 the refrigerant flows to a connection point 176 where the refrigerant is split into two portions, with one portion entering piping segment 150 and the other portion entering piping segment 152.
  • Piping segment 150 includes check valve 148 that allows unidirectional flow from connection point 176 into distributor 162.
  • the refrigerant flows through check valve 148 and into distributor device 162 within section 166 of manifold 106.
  • the refrigerant from piping segment 152 enters distributor device 164 within section 168 of manifold 106.
  • the refrigerant from each distributor device 162 and 164 is then directed through tubes 110 and 112, respectively.
  • refrigerant flows through indoor heat exchanger 130 in a single-pass arrangement where refrigerant flows through each set of tubes 110 and 112 in parallel.
  • the refrigerant absorbs heat from the environment, causing some, or all, of the refrigerant to evaporate, before entering manifold 108.
  • the refrigerant exits manifold 108 and flows through piping segment 154 to a switching valve 136.
  • switching valve 136 is disposed in the cooling position 178 to direct refrigerant from switching valve 136 to reversing valve 34.
  • the refrigerant bypasses piping segment 156.
  • the refrigerant flows to compressor 30 as primarily a low pressure and temperature vapor.
  • the refrigerant is compressed to primarily a high temperature and high pressure vapor that is ready to enter outdoor heat exchanger 129 and begin the refrigeration cycle again.
  • FIGURE 7 depicts heat pump system 128 operating in the heating mode with outdoor heat exchanger 129 operating as a single-pass evaporator and indoor heat exchanger 130 operating as a two-pass condenser.
  • reversing valve 34 is in the heating position 38 and the flow of refrigerant through closed loop 14 is reversed.
  • the switching valves 134 and 136 are switched to heating positions 180 and 182, respectively.
  • the heating positions 180 and 182 enable refrigerant to flow through indoor heat exchanger 130 in a two-pass arrangement and through outdoor heat exchanger 129 in a single-pass arrangement.
  • compressor 30 compresses vapor refrigerant to a primarily high temperature and high pressure vapor.
  • the refrigerant flows through reversing valve 34 to switching valve 136.
  • switching valve 136 is disposed in the heating position 182 to direct refrigerant from switching valve 136 through piping segment 156 to manifold 106 of indoor heat exchanger 130. Accordingly, in the heating mode, the refrigerant bypasses piping segment 154.
  • the refrigerant flows into distributor device 162 within section 166 of manifold 106.
  • Distributor device 162 distributes the refrigerant along the length of section 166 and into tubes 110.
  • Piping segment 150 is also connected to distributor device 162; however, check valve 148 inhibits flow from distributor device 162 into piping segment 150.
  • the refrigerant flows through tubes 110 into manifold 108.
  • the refrigerant then flows through tubes 112 to section 168 of manifold 106. Accordingly, in the heating mode, the refrigerant flows through indoor heat exchanger 130 in two passes where the refrigerant flows through each set of tubes 110 and 112 in series.
  • the refrigerant may be condensed and/or subcooled as the refrigerant transfers heat to the environment.
  • the refrigerant exits indoor heat exchanger 130 through section 168 of manifold 106 and flows through a piping segment 152.
  • the refrigerant then flows through connection point 176 to expansion devices 28 and 29.
  • the pressure differential within the heat pump system 128 inhibits the flow of refrigerant from connection point 176 into piping segment 150, and directs the refrigerant from connection point 176 to expansion devices 29 and 28.
  • the refrigerant expands to become primarily a low pressure and low temperature two-phase refrigerant.
  • connection point 174 where the refrigerant is split into two portions, with one portion entering piping segment 142 and the other portion entering piping segment 144.
  • Piping segment 144 includes check valve 138 that allows unidirectional flow from connection point 174 into distributor device 158.
  • the refrigerant flows through check valve 138 and into distributor device 158 within section 46 of manifold 44.
  • the refrigerant from piping segment 142 enters distributor device 160 within section 48 of manifold 44.
  • the refrigerant from each distributor device 158 and 160 is then directed through tubes 52 and 56, respectively.
  • refrigerant flows through outdoor heat exchanger 129 in a single-pass arrangement where refrigerant flows through each set of tubes 52 and 56 in parallel.
  • the refrigerant absorbs heat from the environment, causing some, or all, of the refrigerant to evaporate, before entering manifold 54.
  • the refrigerant exits manifold 54 and flows through piping segment 146 to switching valve 134.
  • switching valve 134 is disposed in the heating position 180 to direct refrigerant from switching valve 134 to reversing valve 34. Accordingly, in the heating mode, the refrigerant bypasses piping segment 140. From reversing valve 34, the refrigerant flows to compressor 30 as primarily a low pressure and temperature vapor. Within compressor 30, the refrigerant is compressed to primarily a high temperature and high pressure vapor that is ready to enter indoor heat exchanger 130 and begin the refrigeration cycle again.

Landscapes

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

Abstract

La présente invention se rapporte à un système de pompe à chaleur qui comprend un système dirigeant le flux qui permet à un échangeur de chaleur externe de pouvoir être commuté entre un agencement à une seule passe et un agencement à deux passes. Le système de pompe à chaleur comprend un échangeur de chaleur externe, un échangeur de chaleur interne et un système dirigeant le flux des clapets de non-retour et des segments de tuyauterie qui permettent la commutation de l'échangeur de chaleur externe entre l'agencement à une seule passe et l'agencement à deux passes. L'échangeur de chaleur externe peut fonctionner comme un condensateur à deux passes en mode refroidissement et comme un évaporateur à une seule passe en mode chauffage.
PCT/US2012/025496 2011-02-16 2012-02-16 Système de pompe à chaleur doté d'un système dirigeant le flux WO2012112802A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201280009372.XA CN103380335B (zh) 2011-02-16 2012-02-16 具有流动引导系统的热泵系统
US13/967,604 US9752803B2 (en) 2011-02-16 2013-08-15 Heat pump system with a flow directing system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201161443547P 2011-02-16 2011-02-16
US61/443,547 2011-02-16

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US13/967,604 Continuation US9752803B2 (en) 2011-02-16 2013-08-15 Heat pump system with a flow directing system

Publications (2)

Publication Number Publication Date
WO2012112802A2 true WO2012112802A2 (fr) 2012-08-23
WO2012112802A3 WO2012112802A3 (fr) 2013-09-26

Family

ID=45787343

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2012/025496 WO2012112802A2 (fr) 2011-02-16 2012-02-16 Système de pompe à chaleur doté d'un système dirigeant le flux

Country Status (2)

Country Link
CN (1) CN103380335B (fr)
WO (1) WO2012112802A2 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104180709A (zh) * 2014-08-11 2014-12-03 无锡溥汇机械科技有限公司 一种相通容器的液体循环压力控制水箱
WO2019007558A1 (fr) * 2017-07-03 2019-01-10 Audi Ag Installation frigorifique pour véhicule pourvue d'un circuit de réfrigération équipé d'un échangeur thermique et échangeur thermique conçu pour une telle installation frigorifique
DE102018215026A1 (de) * 2018-09-04 2020-03-05 Audi Ag Kälteanlage für ein Fahrzeug mit einem einen zweiflutigen Wärmeübertrager aufweisenden Kältemittelkreislauf sowie Wärmeübertrager und Verfahren zum Betreiben der Kälteanlage
US10625572B2 (en) 2014-03-17 2020-04-21 Mahle International Gmbh Heating/cooling module

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105333642A (zh) * 2014-08-07 2016-02-17 广州市华德工业有限公司 一种冷暖型热泵系统
CN105066519B (zh) * 2015-08-06 2017-12-22 昆山方佳机械制造有限公司 一种干式蒸发器及具有该干式蒸发器的制冷系统
CN109631374A (zh) * 2018-12-04 2019-04-16 天津商业大学 一种具有新型双流程微通道蒸发器的制冷系统
CN109489307A (zh) * 2018-12-04 2019-03-19 天津商业大学 具有双供液管和导气细管的双流程微通道蒸发器

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5085058A (en) * 1990-07-18 1992-02-04 The United States Of America As Represented By The Secretary Of Commerce Bi-flow expansion device
JPH0732460U (ja) * 1993-11-19 1995-06-16 株式会社富士通ゼネラル 空気調和機
JP2002243296A (ja) * 2001-02-20 2002-08-28 Fujitsu General Ltd 空気調和機
KR100908769B1 (ko) * 2005-02-02 2009-07-22 캐리어 코포레이션 병류 열교환기와, 균일한 냉매 유동을 촉진하는 방법
CA2596324A1 (fr) * 2005-02-02 2006-08-10 Carrier Corporation Echangeur de chaleur a ecoulement parallele pour applications de type pompe a chaleur
US20080023182A1 (en) * 2006-07-25 2008-01-31 Henry Earl Beamer Dual mode heat exchanger assembly
CN101600929B (zh) * 2006-11-22 2012-05-09 约翰逊控制技术公司 具有不同管道间隔的多通路热交换器
KR101568200B1 (ko) * 2006-11-22 2015-11-11 존슨 컨트롤스 테크놀러지 컴퍼니 다른 튜브 간격을 갖는 멀티채널 열 교환기
JP5486782B2 (ja) * 2008-08-05 2014-05-07 株式会社ケーヒン・サーマル・テクノロジー エバポレータ
JP4845987B2 (ja) * 2009-03-16 2011-12-28 日本軽金属株式会社 冷暖房空調システム

Non-Patent Citations (1)

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

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10625572B2 (en) 2014-03-17 2020-04-21 Mahle International Gmbh Heating/cooling module
CN104180709A (zh) * 2014-08-11 2014-12-03 无锡溥汇机械科技有限公司 一种相通容器的液体循环压力控制水箱
WO2019007558A1 (fr) * 2017-07-03 2019-01-10 Audi Ag Installation frigorifique pour véhicule pourvue d'un circuit de réfrigération équipé d'un échangeur thermique et échangeur thermique conçu pour une telle installation frigorifique
US11364770B2 (en) 2017-07-03 2022-06-21 Audi Ag Refrigeration system for a vehicle, comprising a refrigerant circuit having a heat exchanger, and heat exchanger for such a refrigeration system
DE102018215026A1 (de) * 2018-09-04 2020-03-05 Audi Ag Kälteanlage für ein Fahrzeug mit einem einen zweiflutigen Wärmeübertrager aufweisenden Kältemittelkreislauf sowie Wärmeübertrager und Verfahren zum Betreiben der Kälteanlage
DE102018215026B4 (de) 2018-09-04 2021-08-26 Audi Ag Kälteanlage für ein Fahrzeug mit einem einen zweiflutigen Wärmeübertrager aufweisenden Kältemittelkreislauf sowie Wärmeübertrager und Verfahren zum Betreiben der Kälteanlage

Also Published As

Publication number Publication date
CN103380335B (zh) 2016-09-14
CN103380335A (zh) 2013-10-30
WO2012112802A3 (fr) 2013-09-26

Similar Documents

Publication Publication Date Title
US9752803B2 (en) Heat pump system with a flow directing system
US7677057B2 (en) Multichannel heat exchanger with dissimilar tube spacing
US7802439B2 (en) Multichannel evaporator with flow mixing multichannel tubes
US8561427B2 (en) Multi-slab multichannel heat exchanger
US9429345B2 (en) Heat-pump chiller with improved heat recovery features
US20100251742A1 (en) Hvac&r system valving
WO2012112802A2 (fr) Système de pompe à chaleur doté d'un système dirigeant le flux
US20120103005A1 (en) Screw chiller economizer system
KR101639814B1 (ko) 냉장 및 냉동 복합 공조시스템
US20100006276A1 (en) Multichannel Heat Exchanger
WO2009018159A2 (fr) Echangeur thermique multicanaux multi-tranches
US20110088883A1 (en) Multichannel heat exchanger with improved flow distribution
JP2010060274A (ja) 相違する流れを有するマルチチャネル熱交換器
WO2007052898A1 (fr) Système de climatisation pour équipement de communication et procédé pour le commander
WO2011005986A2 (fr) Echangeur thermique multicanaux doté d’un espacement d’ailette différent
EP3483523A1 (fr) Appareil de cycle de réfrigération et appareil de climatisation équipé de celui-ci

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12706973

Country of ref document: EP

Kind code of ref document: A2

122 Ep: pct application non-entry in european phase

Ref document number: 12706973

Country of ref document: EP

Kind code of ref document: A2