EP0760453A2 - Klimaanlage mit Unterkühler und in Serie verbundenen Entspannungsvorrichtungen - Google Patents

Klimaanlage mit Unterkühler und in Serie verbundenen Entspannungsvorrichtungen Download PDF

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Publication number
EP0760453A2
EP0760453A2 EP96630051A EP96630051A EP0760453A2 EP 0760453 A2 EP0760453 A2 EP 0760453A2 EP 96630051 A EP96630051 A EP 96630051A EP 96630051 A EP96630051 A EP 96630051A EP 0760453 A2 EP0760453 A2 EP 0760453A2
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EP
European Patent Office
Prior art keywords
liquid
working fluid
vapor
heat exchanger
line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP96630051A
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English (en)
French (fr)
Inventor
Ruddy C. Bussjager
James M. Mckallip
Lester N. Miller
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Carrier Corp
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Carrier Corp
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Publication of EP0760453A2 publication Critical patent/EP0760453A2/de
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    • 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
    • F25B1/00—Compression machines, plants or systems with non-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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • 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
    • F24F3/1405—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 in which the humidity of the air is exclusively affected by contact with the evaporator of a closed-circuit cooling system or heat pump circuit
    • 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
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0417—Refrigeration circuit bypassing means for the subcooler

Definitions

  • This invention relates to compression/expansion refrigeration, and is particularly concerned with air conditioning systems wherein an additional heat exchanger is employed to increase the cooling capacity of the liquid refrigerant that enters the indoor air evaporator, e.g., to increase the amount of latent cooling in the air leaving the evaporator.
  • Single-fluid two-phase air conditioning and refrigeration systems typically employ a compressor that receives the two-phase working fluid as a low temperature, low-pressure vapor and discharges it as a high temperature, high-pressure vapor.
  • the working fluid is then passed to an outdoor condenser coil or heat exchanger, where the heat of compression is discharged from the working fluid to the outside air, condensing the working fluid from vapor to liquid.
  • This high-pressure liquid is then supplied through an expansion device, e.g., a fixed or adjustable expansion valve or a pressure-reducing orifice, and then enters an indoor evaporator coil at low pressure.
  • the working fluid is a bi-phase fluid (containing both liquid and vapor phases), and absorbs heat from the indoor, comfort-zone air, so that the liquid phase is converted to vapor. This completes the cycle, and the vapor returns to the suction side of the compressor.
  • High humidity has been identified as a major contributory factor in the growth of pathogenic or allergenic organisms.
  • the relative humidity in an occupied space should be maintained at 30% to 60%.
  • high humidity can contribute to poor product quality in many manufacturing processes, and can render many refrigeration systems inefficient, such as open freezers in supermarkets. Also high humidity can destroy valuable works of art, library books, or archival documents.
  • a conventional air conditioner as just described can use up most of its cooling capacity to cool the air to the dewpoint (sensible cooling), and will have little remaining capacity for dehumidification (latent cooling).
  • the indoor air temperature is raised to a comfortable level using either a heating element or a coil carrying the hot compressed vapor from the compressor, to raise the temperature (and reduce the relative humidity) of the overcooled air.
  • a heating element or a coil carrying the hot compressed vapor from the compressor to raise the temperature (and reduce the relative humidity) of the overcooled air.
  • more energy is required.
  • a heat pipe is a simple, passive arrangement of interconnected heat exchanger coils that contain a heat transfer agent (usually a refrigerant such as R-22).
  • a heat pipe system can increase the dehumidification capacity of an air conditioning system, and reduce the energy consumption relative to the overcooling/reheating practice described just above.
  • the heat pipe system is attractive because it can transfer heat from one point to another without the need for energy input.
  • One heat exchanger of the heat pipe is placed in the warm air entering the evaporator, and the other heat exchanger is placed in the cold air leaving the evaporator.
  • the entering air warms the refrigerant in the entering side heat exchanger of the heat pipe system, and the refrigerant vapor moves to the leaving side heat exchanger, where it transfers its heat to the leaving air and condenses. Then the condensed refrigerant recirculates, by gravity or capillary action, back to the entering side heat exchanger, and the cycle continues.
  • the heat pipe system built into an air conditioner can increase the amount of latent cooling while maintaining the sensible cooling at the preferred comfortable thermostat setpoint.
  • the standard air conditioning system may not be able to deal effectively with high temperature and high humidity cooling loads.
  • a heat-pipe enhanced air conditioning system cools the entering air before it reaches the air conditioner's evaporator coil.
  • the entering side heat pipe heat exchanger pre-cools the entering air, so that less sensible cooling is required for the evaporator coil, leaving a greater capacity for latent cooling or dehumidification.
  • the indoor supply air leaving the evaporator being colder than the desired temperature, condenses the vapor in the leaving side heat pipe heat exchanger, which brings the supply air temperature back to the desired comfort temperature.
  • the heat pipe arrangement does have certain advantages, such as passivity and simplicity, it has disadvantages as well.
  • the heat pipe is always in circuit, and cannot be simply turned off, even when increased sensible cooling without dehumidification is called for.
  • the indoor air flow can be significantly restricted.
  • a subcooler coil can be used to increase the cooling capacity of the system, by removing additional heat from the liquid refrigerant after the refrigerant leaves the condenser and before it reaches the evaporator coil.
  • the effect will be to reduce the relative humidity of the indoor air.
  • the subcooled refrigerant passes through an expansion device into the evaporator, with the effect that the evaporator draws heat and moisture from the indoor air down to a lower level than without the subcooler. Then, the subcooler coil in the leaving air warms the indoor air back to a comfortable level, but at a reduced relative humidity.
  • the expansion device has to accommodate the different thermodynamic characteristics of the refrigerant liquid entering the evaporator with and without subcooling. This should occur automatically, and without expensive or complex mechanisms.
  • an object of the present invention to provide an air conditioning system with controllable mechanism for enhancing the latent cooling capacity of an air conditioner.
  • a subcooler heat exchanger is positioned on the leaving side of the indoor evaporator coil.
  • the subcooler heat exchanger has an inlet coupled to the outlet side of the condenser heat exchanger, so that the liquid refrigerant at high pressure flows to the subcooler heat exchanger.
  • the latter also has an outlet coupled though a flow restrictor device, and thence through the expansion device to the evaporator coil.
  • a bypass liquid line directly couples the condenser with the expansion device to the evaporator coil, and there is a liquid-line solenoid valve interposed in the bypass liquid line.
  • the liquid-line solenoid valve When normal cooling is called for (i.e., dehumidification is not needed) the liquid-line solenoid valve is open, and the refrigerant bypasses the sub-cooler.
  • both cooling and dehumidification are called for, e.g., when a humidistat signals a high relative humidity condition
  • the solenoid valve is closed, and the liquid refrigerant is routed through the subcooler.
  • this has the effect of sub-cooling the liquid refrigerant in the cold leaving air, which increases the refrigerant cooling capacity.
  • the sub-cooled refrigerant is fed to the evaporator, which cools the indoor air to a desired wet-bulb temperature and condenses moisture to that temperature.
  • the leaving air passes through the subcooler, which brings the leaving indoor air or supply air to the desired indoor comfort temperature.
  • the solenoid When the solenoid is actuated to bypass the liquid refrigerant around the subcooler, the flow restrictor device creates a much higher flow impedance path for the sub-cooled liquid, so the large majority of the liquid refrigerant flows directly from the condenser through the expansion device into the evaporator coil. In this case, the refrigerant liquid is not supercooled, and the expansion device drops the pressure into the two-phase region when the refrigerant enters the evaporator.
  • the solenoid is configured so that, in the event of failure, the fluid flow will be in the bypass mode.
  • the solenoid valve can be line-powered (e.g. 120 v.a.c.) or thermostat powered (e.g. 24 v.a.c.).
  • the flow restrictor can be a fixed aperture device or can be a thermostatic expansion valve, which controls refrigerant flow according to existing conditions to ensure continuous superheat to the suction side of the compressor.
  • the air conditioning apparatus is controlled by a thermostat with a cooling lead that supplies a signal to actuate the compressor whenever a cooling setpoint temperature is reached or exceeded.
  • a humidity control line is coupled to the thermostat cooling lead, and includes a humidistat in series with the liquid line solenoid valve or with a control relay that actuates the solenoid valve.
  • the humidity control lead can also have a low pressure switch that is in fluid communication with the suction side of the compressor for detecting a low-pressure condition on the suction side of the compressor, which could be indicative of frost or ice on the evaporator.
  • the air conditioner can have a two-stage thermostat, where a second cooling lead is energized when a second, higher setpoint is reached.
  • the control for humidity reduction can include a control relay coupled to the second cooling lead, and having power leads that are in series with the humidity control line.
  • the air conditioner can include two separate air conditioning systems, each having its own compressor, condenser, expansion device, evaporator, and subcooler, with one air conditioning system actuated by the first cooling lead and the other air conditioning system actuated by the second cooling lead.
  • Series expansion devices are not limited only to subcooler applications, but can also be used with a standard air conditioning unit. Alternatively, a pair of expansion devices could also be arranged in parallel. Either arrangement permits tailoring of the pressure drop to accommodate the air conditioner and the particular operating conditions.
  • Fig. 1 is a schematic view of an air conditioning system employing a heat-pipe enhancement according to the prior art.
  • Fig. 2 is a schematic view of an air conditioning system employing a subcooler, according to an embodiment of this invention.
  • Fig. 3 shows a thermostatic control circuit employed in connection with an embodiment of this invention.
  • Fig. 4 is a pressure-enthalpy diagram for explaining the operation of this embodiment.
  • Fig. 5 shows a thermostatic control circuit employed in connection with another embodiment of this invention.
  • Fig. 6 is a schematic view of an air conditioning system employing a subcooler, according to a further embodiment of this invention.
  • Fig. 7 is a schematic view of an air conditioning system employing a multiple cell evaporator, without subcooling, according to another embodiment of this invention.
  • an air conditioning system 10 is configured to provide air conditioning and dehumidification to an indoor comfort zone.
  • the system 10 could also be configured as a heat pump to provide heating to the indoor comfort zone and also provide hot water.
  • a compressor 12 receives a refrigerant vapor at low pressure at a suction inlet S and discharges the refrigerant vapor at high pressure from a discharge or pressure port D.
  • the compressed refrigerant vapor proceeds from the compressor along a pressure line 14 to an outdoor condenser heat exchanger 16. In the condenser the refrigerant vapor expels its heat to the outside air, and condenses as a liquid.
  • the liquid refrigerant travels through a liquid line 18 to an expander device 20 and thence into an indoor air cooling coil or evaporator heat exchanger 22.
  • the expander device can be any suitable throttling device which will deliver the refrigerant to the evaporator 22 as a bi-phase (both liquid and vapor) fluid at low pressure.
  • the expander device 20 can be a pair of spaced orifice plates (e.g., so-called "Dixie cups”) brazed into the inlet to the evaporator 22.
  • the evaporator heat exchanger is a coil in which the refrigerant absorbs heat from a stream 24 of indoor air that passes over the coil and is returned to the building indoor comfort space.
  • a vapor line 26 carries the vapor from the evaporator heat exchanger 22 back to the suction port S of the compressor, where the compression-condensation-expansion-evaporation cycle is repeated.
  • the heat pipe arrangement is associated with the cooling coil or evaporator heat exchanger 22, and comprises a pair of heat exchanger coils and interconnecting tubing, with an entering air coil 32 disposed on the indoor air stream 24 on the entering or return side of the evaporator coil 22, and a leaving air coil 34 on the leaving air or supply side of the coil 22.
  • Interconnecting tubing 36 permits transfer of a working fluid (usually a refrigerant) between the two coils 32 and 34.
  • the heat pipe arrangement 30 absorbs heat from the entering room air, at relatively high humidity, removing some of the cooling load from the evaporator coil 22 and transfers the heat to the leaving air.
  • the entering room air in the air stream 24 can have a temperature of 78 degrees (Fahrenheit), and the heat pipe coil 32 reduces the sensible temperature of the entering air to about 69 degrees. This lowers the entering air dry-bulb temperature, and brings the entering air closer to its dewpoint.
  • the evaporator heat exchanger 22 cools the air stream to a temperature of 49 degrees and condenses moisture, which collects in a drip pan (not shown). Then the overcooled leaving air passes through the heap pipe coil 34, and its sensible temperature is restored to a more comfortable level, e.g., 59 degrees.
  • the wet-bulb temperature remains at 49 degrees, so the indoor air relative humidity is reduced well below what would have been achieved without the heat pipe arrangement 30.
  • the heat pipe arrangement as described here has the attractive features of simplicity, requiring no moving parts, relatively low cost, and low maintenance.
  • Heat pipe assemblies can be retrofitted into existing equipment, although in most cases some equipment modification is necessary to fit the coils 32 and 34 into the existing equipment space provided.
  • the heat pipe arrangement is always in line, and cannot be switched off, for example when additional sensible cooling is needed, but dehumidification is not needed or not important.
  • moisture condensation can actually take place on the entering air heat pipe coil 32, causing the condensate to drip into the equipment cabinet.
  • the indoor air stream has to pass through three coils, namely the heat pipe coils 32 and 34 in addition to the evaporator coil 22, thereby increasing the indoor-air fan load.
  • the present invention addresses the problems that are attendant with heat pipe systems, and permits the air conditioning system to achieve additional humidity removal, when needed, but also achieve a standard amount of latent cooling, i.e., more sensible cooling, when humidity control is less important.
  • the air conditioning system includes a sub-cooler assembly 40 for subcooling the liquid refrigerant in the leaving indoor air from the evaporator 22.
  • a sub-cooler branch line 42 that supplies the liquid refrigerant to a subcooler heat exchanger coil 44 that is positioned in the indoor air stream 24 on the leaving side of the evaporator coil 22.
  • This coil 44 cools the condensed liquid refrigerant and supplies the sub-cooled liquid through a sub-cool liquid line 46 to the evaporator.
  • the line 46 includes a flow restrictor 48, in this case a fixed flow restrictor.
  • the subcooled liquid passes in series through the flow restrictor 48, and then through the expansion device 20, to enter the evaporator coil 22 as a bi-phase fluid.
  • a flow restrictor is described in Honnold, Jr. U.S. Pat. No. 3,877,248, although many other flow restriction devices could be employed in this role.
  • Such a fixed flow restrictor can be a so-called accurator, which is a machined brass slug approximately one-half inch (1.2 cm) long with a through-hole of a predetermined diameter.
  • a liquid bypass line 50 couples the liquid line 18 to the expansion device 20 and evaporator coil 22, bypassing the subcooler heat exchanger coil 44 and the flow restrictor 48.
  • the fixed flow restrictor creates a pure pressure drop to bring the refrigerant liquid down to a pressure that is acceptable for the existing expansion device 20. This enables the sub-cooler assembly 40 to be provided as a "drop-in” enhancement or accessory, with little physical impact on the existing system 10.
  • the bypass line 50 and solenoid 52 are used to route the refrigerant liquid around the subcooler, enabling the subcooler assembly 40 to be either "in” or "out” of the circuit. If the liquid line solenoid 52 is open, the subcooler coil 44 is effectively out of the circuit.
  • the refrigerant flow takes the path of least resistance along the bypass line 50, while the flow restrictor 46 creates an impedance to keep the flow through the subcooler coil 44 to an insignificant level.
  • the subcooler coil 44 warms the air leaving the evaporator coil 22 and subcools the liquid refrigerant being supplied from the condenser coil 16.
  • the subcooled refrigerant liquid has its pressure dropped by the flow restrictor 48, and then passes through the throttling device or expansion device 20 and enters the evaporator or cooling coil 22.
  • the indoor air stream is cooled to a suitable low temperature, e.g., 49 degrees F as discussed previously, and moisture is condensed from the indoor air.
  • the subcooler coil 44 warms the leaving air to bring the sensible temperature back to a comfortable level, e.g. 59 degrees.
  • the air conditioner system 10 here also employs a compressor low-pressure switch 54 that is operatively coupled to the vapor return line 26 and senses when compressor suction pressure is too low, for guarding against evaporator freeze-up.
  • thermostat control arrangement for high latent refrigerant control can be explained with reference to Fig. 3.
  • a thermostat device 60 located in the building comfort space is used in connection with a transformer 62 that provides 24 v.a.c. transformer voltage. Line voltage at 120 v.a.c. is also available, and powers the transformer 62.
  • the thermostat has a return lead R to the transformer 62, a fan lead G to the indoor fan relay (not shown) and a cooling lead Y 1 that controls the compressor and outdoor fan contactor (not shown), which actuates the compressor 12 when a predetermined cooling setpoint is reached or exceeded and there is a call for cooling.
  • a humidity control line 64 is tied to the cooling lead Y 1 and connects, in series, the low-pressure switch 54 and a wall-mounted humidistat 66 located in the comfort space.
  • a control relay 68 is also disposed in series in the humidity control line 64, with output leads supplying line voltage to the liquid line solenoid valve 52. However, if the 24 volt transformer 62 has sufficient power, the humidity control line can power the solenoid relay 52 directly.
  • the wall-mounted humidistat 66 directly energizes and de-energizes the bypass liquid line solenoid valve 52 taking the subcooler coil 44 into and out of the refrigerant circuit.
  • the low pressure switch will detect this condition and take the subcooler coil 44 out of circuit, helping to prevent evaporator coil freeze-up.
  • Fig. 3 is a system pressure-enthalpy diagram for explaining the refrigerant heat flow in the system, ignoring general system losses.
  • pressure is along the vertical axis or ordinate, and enthalpy is on the horizontal axis or abscissa.
  • the refrigerant working fluid is R22, and liquid, vapor, and bi-phase regions are generally as labeled.
  • the solid line graph represents the air conditioner mode with the subcooler coil 44 in circuit (high latent cooling), while the dash line graph represents the bypass mode (normal cooling).
  • Point A represents the state of the refrigerant leaving the evaporator coil 22 and entering the compressor 12.
  • Point B represents the state of the refrigerant leaving the compressor and entering the condenser 14.
  • the enthalpy is reduced, largely by condensing into the liquid state yielding up heat to the outside air.
  • the refrigerant having condensed, leaves the condenser 14 and enters the subcooler coil 44.
  • the enthalpy of the refrigerant is reduced by reducing the liquid temperature left of the liquid saturation line.
  • the sub-cooled refrigerant liquid passes to the pressure restrictor 48, and undergoes a pressure reduction to point E, where the liquid enters the throttling device or expanding device 20.
  • the refrigerant enters the evaporator coil 22 as a mixture of liquid and vapor phases at low pressure. As the refrigerant passes through the coil 22, the liquid refrigerant evaporates until only vapor leaves the coil and returns to the suction side of the compressor (Point A).
  • the refrigerant follows the pressure-enthalpy graph shown in broken line in Fig. 4.
  • the refrigerant vapor enters the suction port of the compressor 12 at point A' leaves the compressor discharge port P at point B' and enters the condenser 16. Because the circuit now bypasses the subcooler coil 44 and the flow restrictor 48, the liquid refrigerant enters the expander device 20 at point E' and is released at point F' at reduced pressure into the evaporator coil 22.
  • a thermostat control for a two-stage system is shown in Fig. 5. Elements that correspond to the elements described with reference to Fig. 3 are identified here with similar reference characters, and a detailed description thereof will not be repeated.
  • a two-stage thermostat 160 is associated with the thermostat transformer, and has a return lead R, a fan lead G, and a cooling lead Y 1 as described previously.
  • a second cooling lead Y 2 which becomes actuated when a second temperature setpoint is reached or exceeded that is higher than the setpoint for the cooling lead Y 1 .
  • the low-pressure switch 54, humidistat 66 and control relay are connected as previously on humidity control line 64 which is tied to the cooling lead Y 1 .
  • a second control relay 170 has its actuator connected to the second cooling lead Y 2 and its output leads connected in series in the humidity control line 64.
  • the second stage of cooling will over-ride the high latent subcooler and take it out of operation. This allows the air conditioning system 10 to achieve its full sensible cooling effect. Then, once the air-conditioned space is returned to an acceptable temperature below the upper setpoint, the second stage of cooling is satisfied, and the subcooler is allowed to come back into the circuit whenever the humidistat 66 calls for dehumidification.
  • FIG. 6 A further embodiment of the improved high latent cooling system is shown in Fig. 6.
  • elements that are also common to the air conditioning systems of Figs. 1 and 2 are identified with the same reference numbers, and a detailed description is omitted.
  • the operative difference from the Fig. 2 embodiment is that the fixed flow restrictor 48 is replaced with a thermostatic expansion valve 148.
  • the thermostatic expansion valve, or TXV is a known device that is frequently employed as an expansion valve at the inlet to an evaporator, although in this embodiment the TXV 148 is used to reduce the pressure of the condensed liquid leaving the subcooler coil 44 before it reaches the expansion device 20 associated with the evaporator coil 22.
  • the TXV 148 has an equalizer line 150 coupled to the low-pressure vapor line 26, and a temperature detecting bulb 152 located on the line 26 downstream of the evaporator coil 22 and before the suction port S of the compressor 12.
  • the TXV modulates the flow of the sub-cooled refrigerant liquid in accordance with the refrigerant temperature and suction pressure. This arrangement ensures that there is a constant superheat into the compressor suction, so that there is no compressor flooding.
  • the TXV 148 drops the refrigerant pressure, but keeps the pressure above the point at which a two-phase (liquid and vapor) exists, i.e., approximately at point E of Fig. 4.
  • the downstream expansion device 20 will then function to drop the pressure of the refrigerant fluid entering the evaporator coil into the point of two-phase or choked flow. This permits the subcooler arrangement to accommodate a wide variety of air conditioning and dehumidification loads, while maintaining acceptable operation conditions.
  • the subcooler assembly 40 can be provided as a "drop-in" system modification, requiring very little effort to install, and which will fit easily into the space available in existing air conditioning systems. As moisture condensation takes place only on the existing evaporator coil, no additional apparatus is needed for collection of the condensate.
  • the subcooler assembly only requires bolting on of the subcooler coil 44, installation of the piping represented by the branches 42, 50 and 46, and the rather straightforward electrical connections to the thermostat as shown in Figs. 3 and 5.
  • the indoor fan load is not increased appreciably.
  • FIG. 7 Another embodiment of this invention is shown in Fig. 7, in which elements that are identical to those of the previous embodiments are identified with the same reference characters, and for which a detailed description will be omitted.
  • a standard air conditioning system is provided without the subcooling feature of the previous embodiments.
  • the refrigerant circuit from the compressor 12 through the condenser coil 16 and liquid line 18 is the same as described previously.
  • a multiple circuit evaporator 122 is used, and the liquid line 18 supplies the liquid refrigerant through a header or manifold 121 to respective inlets for the several refrigerant circuits.
  • each of the inlets has a respective expansion device 120.
  • these are fixed expansion devices, for example each device 120 can be constituted by a pair of so-called “dixie cups.”
  • the thermostatic expansion valve or TXV 148 is disposed in the liquid line 18 in advance of the inlet header 121.
  • the TXV 148 has its equalizer line 150 coupled to the low-pressure vapor line 26, and its temperature detecting bulb 152 located on the line 26 downstream of the evaporator coil 22 and before the suction port S of the compressor 12.
  • the TXV modulates the flow of the refrigerant liquid in accordance with the refrigerant temperature and suction pressure.
  • the amount of restriction afforded by the TXV is designed so that there is pure liquid, at a somewhat reduced pressure, arriving at the inlet header 121 and reaching the expansion devices 120.
  • a TXV has been used to throttle liquid refrigerant to a very low pressure to produce a two-phase fluid.
  • the fluid then passed to a refrigerant distributor with a single orifice.
  • the purpose of the distributor was to provide a good mixture of the two-phase fluid equally to the several refrigerant circuits in the evaporator coil.
  • due to distributor configuration, mechanical orientation, or circuit headering it is frequently difficult to obtain a good mix of the two-phase fluid for each of the refrigerant circuits. This resulted in individual cells flooding (from excess liquid refrigerant) or starving (from a lack of liquid refrigerant).
  • each refrigerant circuit within the evaporator had a dixie-cup type expansion device of its own as a means to ensure proper loading of each refrigerant circuit.
  • This approach had the drawback that the pressure drops for each cell could not be throttled to maintain refrigerant conditions at the optimal level entering the compressor. This could cause excessively high of very low return gas superheat to the compressor, which in turn created operational or system reliability problems where there were swings in temperature or evaporator air flow rates.
  • the TXV 148 is employed in series with multiple fixed expansion devices 120, such as dixie cups. Each refrigerant circuit within the evaporator has a dixie cup expansion device of its own. All the expansion devices 120 are supplied with liquid refrigerant from the single TXV 148. As in the subcooler embodiment (Fig. 6) the TXV 148 will provide a pressure drop without changing the liquid refrigerant to a two-phase fluid. The refrigerant that enters the header 121 and reaches the expansion devices 120 is pure liquid, and as such this design ensures proper and even distribution to each device 120. The respective expansion devices 120 then provide the pressure drop to change the liquid to a two-phase fluid.
  • This arrangement can be employed to advantage where the operating conditions, i.e., temperature and evaporator air flow are subject to changes which could bring about low return gas superheat or excessively high return gas superheat at the suction side of the compressor 12.
  • This arrangement is also advantageous in a system in which the compressor load can vary greatly, and thus requires better throttling of refrigerant to maintain proper operating conditions.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Central Air Conditioning (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Air-Conditioning For Vehicles (AREA)
EP96630051A 1995-08-30 1996-08-23 Klimaanlage mit Unterkühler und in Serie verbundenen Entspannungsvorrichtungen Withdrawn EP0760453A2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US52099195A 1995-08-30 1995-08-30
US520991 1995-08-30

Publications (1)

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EP0760453A2 true EP0760453A2 (de) 1997-03-05

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EP96630051A Withdrawn EP0760453A2 (de) 1995-08-30 1996-08-23 Klimaanlage mit Unterkühler und in Serie verbundenen Entspannungsvorrichtungen

Country Status (9)

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EP (1) EP0760453A2 (de)
JP (1) JPH09119749A (de)
KR (1) KR970011615A (de)
CN (1) CN1149692A (de)
AU (1) AU6428696A (de)
BR (1) BR9603559A (de)
DE (1) DE760453T1 (de)
ES (1) ES2098215T1 (de)
MX (1) MX9603136A (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10042830A1 (de) * 2000-08-30 2002-03-14 Menerga Appbau Gmbh Klimagerät
DE20204746U1 (de) * 2002-03-26 2003-08-07 Kreutzfeldt Nils Luftaufbereitungsgerät zur Regulierung der Wärme und der Luftfeuchtigkeit in geschlossenen Räumen
EP1370809A1 (de) * 2001-03-02 2003-12-17 Ebara Corporation Wärmepumpe und entfeuchtungs-klimaanlage
EP1771691A1 (de) * 2004-05-24 2007-04-11 Carrier Corporation Zweiphasen oder unterkühlungs-aufwärmsystem
CN100402947C (zh) * 2006-08-22 2008-07-16 东南大学 恒温除湿装置及方法
WO2013087602A2 (de) 2011-12-16 2013-06-20 Bs2 Ag Wärmetauscher für luftentfeuchtung
CN110131820A (zh) * 2019-05-15 2019-08-16 格力电器（合肥）有限公司 空气调节设备
US20230056774A1 (en) * 2021-08-17 2023-02-23 Solarisine Innovations, Llc Sub-cooling a refrigerant in an air conditioning system

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IT1252704B (it) * 1991-12-20 1995-06-26 Sgs Thomson Microelectronics Struttura di dispositivo a semiconduttore con dissipatore metallico e corpo in plastica avente superfici di contatto a rugosita' controllata e procedimento per la sua fabbricazione
KR100589906B1 (ko) * 2004-07-24 2006-06-19 삼성전자주식회사 공기조화기
JP2009257708A (ja) * 2008-04-21 2009-11-05 Daikin Ind Ltd 熱交換器ユニット
CN105627470B (zh) * 2015-12-30 2018-07-03 同济大学 一种基于过冷再热的空调机组
CN107036194B (zh) * 2017-05-27 2023-04-07 山东美诺邦马节能科技有限公司 高温水冷双冷源除湿新风换气机组
CN107940803A (zh) * 2017-11-21 2018-04-20 珠海格力电器股份有限公司 热泵系统及变频器降温方法
JP7054308B2 (ja) * 2018-10-10 2022-04-13 エスペック株式会社 環境試験装置及び空気調和装置

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* Cited by examiner, † Cited by third party
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JPS6294773A (ja) * 1985-10-18 1987-05-01 松下精工株式会社 空気調和機の冷媒制御装置
JPS63271063A (ja) * 1986-08-20 1988-11-08 Purosupaa Kk ボイラ
JPH0678769B2 (ja) * 1987-04-13 1994-10-05 石川島播磨重工業株式会社 セラミック軸受取付構造
JP3173048B2 (ja) * 1991-07-29 2001-06-04 日本電気株式会社 半導体装置

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10042830A1 (de) * 2000-08-30 2002-03-14 Menerga Appbau Gmbh Klimagerät
EP1370809A1 (de) * 2001-03-02 2003-12-17 Ebara Corporation Wärmepumpe und entfeuchtungs-klimaanlage
EP1370809A4 (de) * 2001-03-02 2006-10-04 Ebara Corp Wärmepumpe und entfeuchtungs-klimaanlage
DE20204746U1 (de) * 2002-03-26 2003-08-07 Kreutzfeldt Nils Luftaufbereitungsgerät zur Regulierung der Wärme und der Luftfeuchtigkeit in geschlossenen Räumen
EP1771691A1 (de) * 2004-05-24 2007-04-11 Carrier Corporation Zweiphasen oder unterkühlungs-aufwärmsystem
EP1771691A4 (de) * 2004-05-24 2009-09-02 Carrier Corp Zweiphasen oder unterkühlungs-aufwärmsystem
CN100402947C (zh) * 2006-08-22 2008-07-16 东南大学 恒温除湿装置及方法
WO2013087602A2 (de) 2011-12-16 2013-06-20 Bs2 Ag Wärmetauscher für luftentfeuchtung
CH705909A1 (de) * 2011-12-16 2013-06-28 Bs2 Ag Wärmetauscher für Luftentfeuchtung.
WO2013087602A3 (de) * 2011-12-16 2013-09-26 Bs2 Ag Wärmetauscheranodrung zur luftentfeuchtung
CN110131820A (zh) * 2019-05-15 2019-08-16 格力电器（合肥）有限公司 空气调节设备
US20230056774A1 (en) * 2021-08-17 2023-02-23 Solarisine Innovations, Llc Sub-cooling a refrigerant in an air conditioning system

Also Published As

Publication number Publication date
AU6428696A (en) 1997-03-06
CN1149692A (zh) 1997-05-14
JPH09119749A (ja) 1997-05-06
ES2098215T1 (es) 1997-05-01
KR970011615A (ko) 1997-03-27
BR9603559A (pt) 1998-05-19
MX9603136A (es) 1997-03-29
DE760453T1 (de) 1997-09-11

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