US3589437A - Heat pump system air conditioners - Google Patents

Heat pump system air conditioners Download PDF

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US3589437A
US3589437A US887096A US3589437DA US3589437A US 3589437 A US3589437 A US 3589437A US 887096 A US887096 A US 887096A US 3589437D A US3589437D A US 3589437DA US 3589437 A US3589437 A US 3589437A
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Prior art keywords
refrigerant
heating means
heating
terminal
electric heater
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English (en)
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Kunihiro Shoji
Satoru Sato
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Daikin Industries Ltd
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Daikin Industries Ltd
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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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/03—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by mounting arrangements
    • F24F1/031—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by mounting arrangements penetrating a wall or window
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/032—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by heat exchangers
    • F24F1/0323—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/0373—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by heating arrangements
    • F24F1/0375—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing characterised by heating arrangements with additional radiant heat-discharging elements, e.g. electric heaters
    • 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
    • F24F3/001—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 in which the air treatment in the central station takes place by means of a heat-pump or by means of a 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle

Definitions

  • a conventional heat pump system air conditioner which is singly usable for both cooling and heating by operating the refrigeration cycle in one way or another, involves a number of problems when used as a heater because of differences in the inside volumes of the evaporator and condenser, the area of the heat exchangers and the rate of air passing in the heat exchanger, between the heating operation and the cooling operation, which occur as a result of operating the refrigeration cycle in a reverse way, and also because of the temperature and the moisture of the room to be heated, the outdoor temperature and moisture conditions and the use of different elements such as an auxiliary heater and controller. Namely,
  • Another method which has been employed heretofore is to provide an electric heater of small capacity on the indoor heat exchanger, which generates heat just sufi'lcient enough to make up the lack of heating capacity of the conditioner. This method is again unsatisfactory in respect of danger of fire, because the electric heater directly heats air.
  • refrigerant regulating means are unexceptionally only capable of maintaining a required quantity of refrigerant in the cooling operation or in the heating operation and only render the construction of the conditioner unnecessarily complicated and the size of the same unnecessarily large.
  • the air passing through the indoor heat exchanger is reduced to none or decreased and accordingly the heat absorption from the air inside the room is stopped or decreased.
  • the air inside the room is also cooled by both the indoor heat exchanger and the outer panel of the conditioner, though the cold draft into the room is stopped or decreased, and hence the inside temperature of the room is lowered to below the comforable limit, which has been the fatal drawback of the method.
  • the first object of the invention is to provide a heat pump system air conditioner utilizing refrigeration cycle, in which refrigerant-heating means consisting of an electric heater, not exposed to air, is provided at an intermediate position of the refrigerant passage line of an indoor heat exchanger for heating a refrigerant, thereby to form in the heating operation such a refrigeration cycle wherein a high-pressure superheated gas, discharged from a compressor, is partially or wholly condensed and liquefied at a portion of the indoor heat exchanger into a wet vapor and after the wet vapor is reevaporated by the refrigerant-heating means, the resultant gas is again condensed and liquefied at the remaining portion of the indoor heat exchanger, the subcooling refrigerant thus liquefied flowing into an expansion member wherein it is reduced in pressure, and then evaporated and gasified in an outdoor heat exchanger and returned into the compressor
  • the second object of the invention is to provide a heat pump system air conditioner of the character described above, in which said refrigerant-heating means is provided extending therethrough with a mounting tube or tubes having one end open to the outside of one end of one end of the refrigerantheating means and the other end closed or open to the outside of the other end of said refrigerant-heating means, in which are disposed an electric heater and an overheat preventing member consisting of a thermostat or a temperature fuse which is provided for the purpose of preventing the refrigerant from being decomposed or deteriorated by contact with the outer peripheral surface of said mounting tube when the temperature of said mounting tube becomes abnormally high, whereby mounting of said parts in the mounting tube and replacement of the same due to failure are facilitated.
  • the third object of the invention is to provide a heat pump system air conditioner of the character described above, in which said mounting tube in said refrigerant heating means is provided with fins on the outer peripheral surface thereof which is in contact with the refrigerant, so as to lower the temperature of said surface and thereby to prevent decomposition and deterioration of the refrigerant by the heat of the mounting tube and also to increase the refrigerant-heating surface area to heat the refrigerant effectively and moderately
  • the fourth object of the invention is to provide a heat pump system air conditioner of the character described above, in which an electric circuit of the air conditioner is so designed that the electric heater of said refrigerant-heating means will be actuated, in the heating operation, only when said compressor is in operation, whereby local heating of the refrigerant by the electric heater when the refrigerant is held stationary upon deenergization of the compressor can be avoided and hence the danger of the refrigerant partially being decomposed and deteriorated is eliminated.
  • the fifth object of the invention is to provide a heat pump system air conditioner of the character described above, in which the electric circuit of the air conditioner is so designed that the refrigerant-heating means is held energized, not only during the normal heating operation but also during a defrosting operation for eliminating the frost attached to the outdoor heat exchanger, which is effectuated by the cooling cycle, whereby the refrigerant present in the indoor heat exchanger, which acts as evaporator in the defrosting operation, is heated to elevate the evaporating temperature thereof and to prevent the surface temperature of said indoor heat exchanger from lowering to thereby avoid a cold draft blowing into the room, and also the defrosting period is shortened as a result of the condensation temperature in the outdoor heat exchanger being elevated by the evaporating temperature rise.
  • the sixth object of the invention is to provide a heat pump system air conditioner of the character described above, in which said electric heater for heating the refrigerant is directly inserted into the refrigerant of the refrigerant-heating means and the danger of electricity leakage is avoided by making use of the electricity insulating effect of the refrigerant.
  • the seventh object of the invention is to provide heat pump system air conditioner of the character described above, in which in the heating operation the refrigerant is supplied into the refrigerant-heating means through a conduit communicating with the lower portion of the cavity in the refrigerant-heating means and discharged through a conduit communicating with the upper portion of the same, so that excess refrigerant may be stored in said refrigerant-heating means in the liquid form during the heating operation, whereby the necessity for providing a separate refrigerant storage tank can be eliminated and the refrigerant is heated efiieiently by the electric heater during its residence in said refrigerant-heating means, enabling the effect of heating the refrigerant to be fully demonstrated, which is the first object of the present invention.
  • the eighth object of the invention is to provide a heat pump system air conditioner of the character described above, particularly in the preceding paragraph, in which when the outdoor heat exchanger has been frosted, the refrigeration cycle is switched from the heating cycle to the cooling cycle, whereupon the pressure inside the refrigerant heating means is reduced and the liquid refrigerant stored therein is evaporated abruptly and sucked into the compressor, and thus the introduction of the refrigerant gas into and discharge of the compressed refrigerant gas from the compressor can smoothly be effected and the defrosting period can be shortened ac cordingly.
  • the ninth object of the invention is to provide a heat pump system air conditioner of the character described above, in which the electric circuit of the air conditioner is so designed that a fan is rotated at a low speed when the temperature of the discharging air is low at the start of the heating operation and is rotated at a high speed when the temperature of the discharging air has reached to a desired level, so that air is blown into the room at a low rate in the initial state of the heating operation when the condensation temperature of the refrigerant in the indoor heat exchanger is low and the temperature of the air discharged from the air conditioner is low, so as to minimize the undesirable effect of cold draft, whereas when the condensation temperature in the indoor heat exchanger has risen sufficiently and the temperature of the air blown into the room has been elevated high enough not to cause cold draft, the rotational speed of the fan is increased to promote heating of the room.
  • the tenth object of the invention is to provide a heat pump system air conditioner of the character described above, in which the electric circuit of the air conditioner is so designed that the electric heater provided in the refrigerant-heating means will be energized, in the heating operation, only when the room temperature is low and will not be energized when the room temperature is high, so that said electric heater may effectively utilized.
  • HO. 1 is a piping diagram of the refrigeration cycle of the heat pump system air conditioner according to the present invention
  • FIG. 2 is a mollier diagram of the air conditioner
  • FIG. 3 is an electric wiring diagram of the air conditioner
  • FIG. 4 is a schematic view showing the construction of the air conditioner
  • FIG. 5 is a cross-sectional view of one form of the refrigerant-heating means comprising a mounting tube or tubes, and an electric heater and an overheat preventing member disposed in each mounting tube, and having a higher conduit and a lower conduit connected horizontally to the opposite end walls of said refrigerant-heating means;
  • FIG. 6 is a cross-sectional view of another form of the refrigerant-heating means comprising a mounting tube or tubes and an electric heater disposed in each mounting tube, and having a lower conduit and a higher conduit connected vertically to both end portions of the refrigerant-heating unit;
  • FIG. 7 is a cross-sectional view of still another form of the refrigerant-heating means comprising a mounting tube or tubes and an electric heater disposed in each mounting tube, and having two lower conduits connected in parallel relation to both end portions of the refrigerant-heating means and a higher conduit connected to the central portion of the refrigerant-heating means;
  • FlG. 8 is a cross-sectional view of still another form of the refrigerant-heating means comprising a mounting tube or tubes and an electric heater directly wound on each mounting tube;
  • FIGS, 9 to 12 are diagrams respectively showing the characteristics of the air conditioner, in which FIG. 9 is a heating capacity characteristic diagram showing the relationship between the outdoor temperature, and the power consumption and the heating capacity;
  • FIG. 10 is a liquid refrigerant storage effect characteristic of the refrigerant-heating means diagram showing the relationship between the outdoor temperature and the gas intake tube temperature;
  • H6. 11 is a defrosting test characteristic diagram showing the relationship between the time elapsed in the operation and the discharging air temperature.
  • FIG. 12 is an overheat preventing member of the refrigerant heating means operation test characteristic diagram showing the relationship between the time elapsed after the stoppage of the compressor and the fan and the temperature.
  • the path of the refrigerant in heating operation forms a refrigeration refrigerant-heating as indicated by the solid line arrows which extends from a compressor l to four-way changeover valve 2, a first indoor heat exchanger 3, a lower conduit 10, a refrigerant-heating means 6, a higher conduit ill, a second indoor heat exchanger 3", a capillary tube 4, an outdoor heat exchanger 5, the four-way changeover valve 2, an accumulator l4! and back to the compressor 1, and in the cooling operation, forms a reverse refrigeration cycle as indicated by the dotted line arrows, with the position of the four-way changeover valve 2 being changed upon energization of the electromagnetic coil thereof.
  • a refrigerant heating means 6 is provided at an intermediate position between the first indoor heat exchanger 3' and the second indoor heat exchanger 3" which together form an indoor heat exchanger 3.
  • the high temperature, high-pressure refrigerant gas discharged from the compressor ll (condition B in FIG. 2) is sent through the four-way changeover valve 2 into the first indoor heat exchanger 3', wherein it is partially condensed to form a wet vapor (condition C in F [v 2) while imparting heat to the indoor, and then admitted into the refrigerant-heating means 6.
  • the gaseous refrigerant flows through the refrigerant-heating means 6 but the liquid refrigerant is accumulated in the refrigerant-heating means and heated by an electric heater 7 provided therein and partially evaporated (condition D in FIG. 2).
  • the refrigerant may be entirely liquefied in the first indoor heat exchanger 3, instead of being partially liquefied as stated above.
  • the refrigerant-heating means 6 will be described in detail hereunder:
  • the refrigerant-heating means 6 thereshown has a mounting tube 8 extending through the center thereof, and an electric heater 7 is inserted into the mounting tube 6 through one end, while an overheat-preventing member 9, such as a thermostat or a temperature fuse, is inserted into the tube through the other end, which automatically controls the current supply to the electric heater 7 upon detecting the temperature of the mounting tube 8.
  • Numeral l3 designates fins provided on the outer peripheral surface of the mounting tube 8 to increase the heat-exchanging area.
  • a lower conduit 10 which extends horizontally for communication with the first indoor heat exchanger, while to the upper portion of the other end of the refrigerant-heating means is connected a higher conduit III for communication with the second indoor heat exchanger.
  • the refrigerant is introduced into the refrigerant-heating means 6 through the higher conduit 11 and discharged therefrom through the lower conduit 10, so that the refrigerant is not allowed to be accumulated in the refrigerant-heating means 6.
  • the refrigerant is introduced into the refrigerantheating means 6 through the lower conduit 10 and discharged through the higher conduit llll, so that a predetermined quantity of the refrigerant is accumulated in the refrigerant-heating means 6 (up to the level a of the underside of the higher conduit ll).
  • FIG. 6 shows another form of the refrigerant-heating means in which a mounting tube 3 having one end closed is horizontally inserted into the refrigerant-heating means 6 and an electric heater 7 is inserted into the mounting tube 8 through the open end thereof.
  • a lower conduit l0 l4 which extends vertically for communication with the first indoor heat exchanger 3'
  • a higher conduit 11 which also extends vertically for communication with the second indoor heat exchanger 3".
  • the refrigerant introduced into the refrigerant-heating means 6 through the lower conduit 10 is accumulated therein up to the level a of the top end of the higher conduit Ill.
  • FIG. 8 shows still another form of the refrigerant-heating means.
  • a hollow mounting tube 8 having an electric heater 7 wound therearound is inserted into the refrigerant-heating means 6 through one end thereof, and the root of the mounting tube and said end of the refrigerant-heating means are soldered together to provide a liquid-tight sealing l2 or 12'.
  • a higher conduit II is connected to the top wall of the refrigerant-heating means 6, while a lower conduit 10 is connected horizontally to the other end of said refrigerantheating means in coaxial relation thereto.
  • the refrigerant introduced into the refrigerant-heating means 6 through the lower conduit 10 is directly heated by the electric heater 7 and discharged therefrom through the higher conduit 11.
  • the electric circuit of the air conditioner includes an operating switch SW by which the operation of the air conditioner is switched from one condition to another among "Off,” Fan,” High Cool,” Low Cool, High Heat,” and Low Heat.
  • the operating switch SW has a power source primary terminal b, a secondary terminal 11 which is connected with the primary terminal b during the High Heat” and Low Heat” operations, and an other secondary terminal 1' which is connected with the primary terminal b during the High Heat operation only.
  • the primary terminal b of the operating switch SW is connected with a terminal X of a power source, whereas the secondary terminal h thereof is connected with a closing terminal n of a temperature controller TC for controlling the operation of the compressor, which closing terminal is opened when the room temperature is high and closed when the room temperature is low.
  • a contact p of the temperature controller TC is connected with the other terminal Y of the power source through a compressor motor MC.
  • An electromagnetic coil MR of an electromagnetic relay for controlling the operation of the electric heater 7 is connected in parallel with the compressor motor MC.
  • the electric heater 7, inserted into the refrigerantheating means 6, is energized only when the compressor is in operation in the heating cycle.
  • the operating switch SW is also provided with a secondary terminal f which is connected with the primary terminal b during the cooling operation only.
  • the secondary terminal f connected with source terminal Y through an electromagnetic coil SV of the four-way change over valve 2 which switches the refrigeration cycle to the cooling cycle when energized and to the heating cycle when deenergized.
  • the secondary contact f of the operating switch SW is connected with a closing contact t of a defrosting switch DC which contact t is closed when the outdoor heat exchanger 5 is frosted and opened when the same is not frosted.
  • a pole contact x of the defrosting switch DC is connected with the source terminal X. Because of the construction of the operating circuit as described above, when the operating switch SW is in the Heat" position, the four-way changeover valve 2 is held in the position of cooling cycle and the electric heater 7 is energized.
  • the operating switch SW is provided with a primary terminal a and a secondary terminal d which will be connected with said primary terminal a only in the heating operation.
  • the primary terminal a is connected with the source terminal X and the secondary terminal d of the operating switch SW is connected with a pole contactj of a switch TC which controls the number of revolutions ofa fan according to the temperature of the refrigerant gas discharged from the compressor 1 or the temperature of the air blown into the room.
  • a closing contact k of the switch TC which is closed when the discharging air temperature is low and opened when the discharging air temperature is high, is connected with a low speed rotation tenninal y of a fan motor FF.
  • a closing contact I of the switch TC is connected with a high speed rotation ter minal y, said closing contact I being opened when the room temperature is low and closed when the room temperature is high.
  • a common terminal z of the fan motor is connected with the source terminal Y.
  • the circuit connecting the secondary terminal i of the operating switch SW with the electric heater 7 has inserted therein a temperature controller TC which closes the circuit to energize the electric heater 7 when the room temperature is low and opens the same to deenergize the electric heater when the room temperature is high.
  • the air conditioner of the present invention having the construction described in detail hereinabove, has the following advantages: First of all, by the provision of the refrigerant heating unit 6, the heating capacity of the air conditioner is increased by the heat generated by the electric heater 7, as compared with the conventional heat pump type air conditioner. Namely, in FIG. 2, as contrasted to the heating capacity of the conventional air conditioner which is [(i,,i,,) X the quantity of the refrigerant circulated], that of the present air conditioner is [(i,,i X the quantity of the refrigerant circulated greater than the former and is (i i )+(i,,i X the quantity of the refrigerant circulated], which represents a marked increase in the heating capacity.
  • the electric heater 7 is disposed within the mounting tube 8 of the refrigerant-heating means 6 and the heated portion of the mounting tube 8 is contact with the liquid refrigerant for exchanging heat with the liquid refrigerant as shown in FIGS. 5,6, and 7. Therefore, the heat transfer rate is high and further there is no danger of fire as the heater is not directly exposed to air.
  • such arrangement facilitates removal, repair and replacement of the electric heater 7 upon failure of said electric heater.
  • the overheat preventing member 9 is provided in the mounting tube 8 adjacent the electric heater 7. Furthermore, since the liquid refrigerant is heated by the electric heater 7, the air in the vicinity of the indoor heat exchanger 3 will not be heated abnormally, which ensures the safety of the air conditioner.
  • the safety will be further ensured if a heat-insulating material is provided around the outer surface of the refrigerant-heating means 6.
  • the overheatpreventing member 9 for controlling the current supply to the electric heater 7 can detect the temperature of the mounting tube 8 by direct contact therewith, so that it is much more sensitive in detecting ability and more reliable in operation than the conventional safety device which detects the temperature through the intermediary of air, and hence the danger of fire can be eliminated more positively.
  • the electromagnetic relay MR is inserted in the electric circuit of the compressor 1 so that the electric heater 7 may be energized only after the compressor 1 is placed in motion. Therefore, in no case is the electric heater 7 energized, with the compressor being inoperative. If the refrigerant stops flowing or the flow rate of the refrigerant is reduced, less heat is transferred to the refrigerant and more heat is transferred to the overheat-preventing member 9 from the electric heater 7, so that the current supply to the electric heater 7 is automatically interrupted by the action, for example, of a bimetal of said member 9.
  • the electric heater 7 Since the electric heater 7 is surrounded by the liquid refrigerant, the remaining heat of the electric heater 7 is absorbed by the liquid refrigerant after the heat pump operation has been stopped, whereby the subsequent temperature rise of the refrigerant and lubricant is prevented to avoid deterioration and thermal decomposition of the same, providing for safety operation of the air conditioner.
  • the refrigerant-heating means 6 are connected one ends of the lower conduit 10 and the higher conduit 11, the other ends of which are connected to the first indoor heat exchanger 3' and the second indoor heat exchanger 3 respectively, and when the air conditioner is in the cooling cycle, with the refrigerant circulating in the directions of the dotted line arrows in FIG.
  • the refrigerant is admitted into the refrigerant-heating means 6 through the higher conduit 11 and discharged therefrom through the lower conduit 10, so that it is not permitted to reside in said refrigerant-heating means, whereas when the air conditioner is in the heating cycle with the refrigerant circulating in the directions of the solid lines arrows, the refrigerant is enters the refrigerant-heating means 6 through the lower conduit 10 and leaves the same through the higher conduit 11, so that it is accumulated in said heating means up to the level of the higher conduit as indicated by the phantom line a in FIGS. 5 to 7.
  • the quantity of refrigerant in the heating operation is automatically controlled by the refrigerant-heating means 6 which holds excess refrigerant therein, to the level actually required for the heating operation and thereby return flow of the liquid refrigerant into the compresssor l is prevented when the outside temperature is low.
  • the refrigerant-heating means of the construction shown in FIG. 6 is mounted slantingly.
  • the quantity of the refrigerant residing in the refrigerant-heating means is determined by the position of the open top end of the higher conduit 11 and hence a calculated quantity of the refrigerant cannot be reserved in the refrigerant-heating means 6, which will result in unsatisfactory heating operation.
  • Such disadvantage can be obviated by employing the refrigerant-heating means of the construction shown in FIG. 7.
  • a higher conduit 11 is provided centrally of the heating means and two lower conduits 10 are provided parallelly at the opposite end portions of the same, so that the quantity of the refrigerant residing in the heating means is always constant.
  • the air conditioner of the present invention also has such a remarkable advantage that the defrosting period can drastically be shortened as compared with the conventional one. Namely, when the outside temperature is low, the evaporating temperature is lowered and the surface temperature of the outdoor heat exchanger 5 drops below the freezing point, with the accompanying result that the surface of said outdoor heat exchanger is frosted. In this case, the operation of the air conditioner is switched to the cooling cycle to remove the frost from the outdoor heat exchanger.
  • the electric heater 7 is energized to heat the refrigerant and the refrigerant is not accumulated in the refrigerant heating means during the period of cooling cycle. Therefore, the gaseous refrigerant heated by the electric heater 7 is forcibly returned to the compressor 1, so that defrosting can be attained in a short period of time, which in the past has taken a long time due to a gasless operation.
  • the defrosting operation in normally performed upon stopping the fan. This is for the purposes of avoiding a cold draft and easing the defrosting operation conducted at the outside temperature below the freezing point.
  • the defrosting operation is performed with the fan being held stationary, the capacity of the indoor heat exchanger 3 becomes shorted, with the result that the evaporating temperature and, therefore, the condensating temperature are lowered. Therefore, the quantity of heat available for defrosting is small.
  • the liquid refrigerant which has not been evaporated in the indoor heat exchanger 3 objeetionably flows back into the compressor 1.
  • heat is imparted to the refrigerant in the indoor heat exchanger 3, so that the evaporating temperature is not lowered, recycling of the liquid refrigerant into the compressor 1 can be avoided, the condensating temperature is not lowered, and a large quantity of heat is available for defrosting.
  • the defrosting operation can be accomplished in a short period of time and the efficiency of the heating operation can be enhanced.
  • Still another advantage of the present air conditioner is that occurrence of a cold draft can completely be avoided in the heating operation, since the electric circuit thereof is so designed that the speed of the fan is controlled according to the room temperature.
  • Another important advantage of the present air conditioner is that the room can be heated efficiently with less power consumption, due to the fact that in the heating operation the air conditioner is operated only in the heating cycle,. with the electric heater 7 being energized when the room temperature is low and is deenergized when the room temperature is high.
  • FIG. 9 shows the relationship between the outdoor temperature, and the heating capacity and power consumption, in each of the cases when the heat pump only was used and the case when both the heat pump and the heater were used.
  • the room-heating capacity was measured by measuring the temperature rise of cold water coil placed in the room, using the room-type calorimeter specified in Appendix I of C-6912 (Electric Air Conditioners) of Japan Industrial Standards.
  • the diagram of FIG. 9 shows that a desired heating capacity of 2,240 kcaL/h (60 cycle) at an outdoor temperature of -2 C was obtained by incorporating in the refrigerant heating means an electric heater having a capacity of 0.7 kw. This capacity of the electric heater is much smaller as compared with a capacity of 2.6 kw. which is required for obtaining the same heating capacity with an electric heater only.
  • FIG. 10 shows the effect of reserving the refrigerant in the refrigerant-heating means 6.
  • the temperature of the suction pipe to the compressor was measured at the locations indicated.
  • the refrigerant is reserved in the refrigerant-heating means, the refrigerant is sucked into the compressor in the form of a superheated gas at a lower outdoor temperature than when the refrigerant is not reserved.
  • FIG. 11 shows the condition of the present air conditioner in the defrosting operation.
  • the defrosting operation is completed in about minutes when the operation is performed under the conditions specified in ARI (Air-Conditioning and Refrigeration Institute) Specification.
  • ARI Air-Conditioning and Refrigeration Institute
  • the defrosting operation period according to the present invention is about 5 minutes which is much smaller than percent of the specified value.
  • FIG. I2 is concerned with the safety of the refrigerant-heating means and shows how the inside and outside temperatures of the refrigerant-heating means change with time, when the fan and the compressor are stopped.
  • the function of the overheat-preventing member was tested under such severe conditions that the electric heater is held energized while the fan and the compressor are held inoperative, which will not actually occur.
  • the temperature of the heater surface in contact with the refrigerant, which is highest, was measured by means of a thermocouple welded to said surface. The result was that the temperature of the heater surface reached the highest value and was 130 C. 2 minutes after the heater had been deenergized by the action of the overheat-preventing member. It is revealed in the literatures relating to refrigerant that such temperature will not have a practical effect of deteriorating the refrigerant and lubricant at all if it lasts only for a short period.
  • a heat pump system air conditioner having a heat pump system cooling and heating circuit operating in a refrigeration cycle and composed of a compressor 1, four-way changeover valve 2, an indoor heat exchanger 3 consisting of a first indoor heat exchanger 3 and a second indoor heat exchanger 3"an expansion member (4), an outdoor heat exchanger 5 and an accumulator 14, in which a refrigerant-heating means (6) having an electric heater 7 inserted therein in such a manner that it is not exposed to air is provided between the first indoor heat exchanger 3' and the second indoor heat exchanger 3"so that the heating operation has a refrigerant partially or wholly condensed in the first indoor heat exchanger 3' is heated and evaporated in said refrigerant-heating means and then condensed again in the second indoor heat exchanger 3"whereby the air circulating in a room to be heated can be heated by the heat generated by the condensation of the gaseous refrigerant in the indoor heat exchanger 3 plus the heat generated by the electric heater 7.
  • a heat pump system air conditioner as defined in claim I wherein in the refrigerant-heating means a conduit for introducing the refrigerant from the first indoor heat exchanger 3' into the refrigerant-heating means 6 therethrough is open in the lower portion of said refrigerant-heating means 6, whereas a conduit 11 for discharging the refrigerant from the refrigerant-heating means 6 into the second indoor heat exchanger (3") therethrough is open in the upper portion of the refrigerant-heating means 6, whereby in the heating operation the quantity of the refrigerant substantially acting as refrigerant in the refrigeration cycle is reduced by storing the liquid refrigerant in the refrigerant-heating means 6 to enhance the efiiciency of the heating operation, whereas in the cooling operation the refrigerant is not allowed to reside in the refrigerant-heating means 6 so that cooling operation can be attained at a high efficiency.
  • an overheat-preventing member 9 such as a thermostat or a temperature fuse for preventing overheating of the outer peripheral surface of said mounting tube 8 in contact with the refrigerant
  • radiator fins 13 are provided on the outer peripheral surface of said mounting tube 8.
  • an operating switch SW is provided to switch the operation of the air conditioner from one another among the conditions ofOff," Fan, I-Iigh Cold,” Low Cold, High Heat” and Low Heat
  • said operating switch SW being provided with a primary terminal b connectedto one terminal X of a power source and a secondary terminal I: or i which will be connected to said primary terminal b only in the heating operation, said secondary terminal h or i being connected with a closing contact n of a temperature controller TC for controlling the operation of the compressor, which closing contact n is opened when the room temperature is high and closed when the room temperature is low, a pole contact p of said temperature controller TC being connected with the other power source terminal Y through a compressor motor MC, said compressor motor MC having connected in parallel thereto an electromagnetic coil MR of an electromagnetic relay for controlling the operation of the electric heater 7, and
  • said secondary terminal h of i of said operating switch SW I being connected with the power source terminal Y through the electric heater 7 and the contact MR is parallel to the circuit extending from said secondary terminal h or i to the power source terminal Y through said compressor motor MC, which contact MR is closed when the electromagnetic coil MR is energized and opened when the electromagnetic coil is not energized, whereby the electric heater (7) inserted in the refrigerant-heating means 6 is energized only when the compressor is in motion in the heating operation.

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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)
  • Defrosting Systems (AREA)
  • Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
US887096A 1968-12-24 1969-12-22 Heat pump system air conditioners Expired - Lifetime US3589437A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11320568 1968-12-24
JP180769 1968-12-28

Publications (1)

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US (1) US3589437A (ko)
BE (1) BE743606A (ko)
FR (1) FR2027054A1 (ko)
GB (1) GB1265229A (ko)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3777508A (en) * 1971-09-06 1973-12-11 Matsushita Electric Ind Co Ltd Heat pump type air conditioning systems
FR2381258A1 (fr) * 1977-02-18 1978-09-15 Electric Power Res Inst Pompe a chaleur comportant un element chauffant auxiliaire
US4313307A (en) * 1977-09-12 1982-02-02 Electric Power Research Institute, Inc. Heating and cooling system and method
US5473907A (en) * 1994-11-22 1995-12-12 Briggs; Floyd Heat pump with supplementary heat
US20050097914A1 (en) * 2003-11-10 2005-05-12 Jonathan Bruce Heating / cool compressor
US20080034777A1 (en) * 2006-08-11 2008-02-14 Larry Copeland Gas engine driven heat pump system with integrated heat recovery and energy saving subsystems
US20090114732A1 (en) * 2007-11-02 2009-05-07 Tube Fabrication Design, Inc. Multiple cell liquid heat pump system and method
US9534818B2 (en) 2012-01-17 2017-01-03 Si2 Industries, Llc Heat pump system with auxiliary heat exchanger
WO2017192612A1 (en) * 2016-05-02 2017-11-09 Wong Lee Wa Air conditioning and heat pump tower with energy efficient arrangement
US20180363278A1 (en) * 2012-10-09 2018-12-20 Philip Heller Humidity collector apparatus

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2718265C3 (de) * 1977-04-25 1982-06-16 Burger, Manfred R., 8023 Pullach Verfahren zum wahlweisen Heizen oder Kühlen eines Fluidstromes und Wärmepumpe zu dessen Durchführung
US4311192A (en) * 1979-07-03 1982-01-19 Kool-Fire Limited Heat-augmented heat exchanger
CN107702391B (zh) * 2017-10-11 2023-07-21 珠海格力电器股份有限公司 一种用于化霜的冷媒加热装置和空调系统

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3308877A (en) * 1965-07-01 1967-03-14 Carrier Corp Combination conditioning and water heating apparatus

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3308877A (en) * 1965-07-01 1967-03-14 Carrier Corp Combination conditioning and water heating apparatus

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3777508A (en) * 1971-09-06 1973-12-11 Matsushita Electric Ind Co Ltd Heat pump type air conditioning systems
FR2381258A1 (fr) * 1977-02-18 1978-09-15 Electric Power Res Inst Pompe a chaleur comportant un element chauffant auxiliaire
US4313307A (en) * 1977-09-12 1982-02-02 Electric Power Research Institute, Inc. Heating and cooling system and method
US5473907A (en) * 1994-11-22 1995-12-12 Briggs; Floyd Heat pump with supplementary heat
US20050097914A1 (en) * 2003-11-10 2005-05-12 Jonathan Bruce Heating / cool compressor
US20090173486A1 (en) * 2006-08-11 2009-07-09 Larry Copeland Gas engine driven heat pump system with integrated heat recovery and energy saving subsystems
US7503184B2 (en) 2006-08-11 2009-03-17 Southwest Gas Corporation Gas engine driven heat pump system with integrated heat recovery and energy saving subsystems
US20080034777A1 (en) * 2006-08-11 2008-02-14 Larry Copeland Gas engine driven heat pump system with integrated heat recovery and energy saving subsystems
US20090114732A1 (en) * 2007-11-02 2009-05-07 Tube Fabrication Design, Inc. Multiple cell liquid heat pump system and method
US8282017B2 (en) 2007-11-02 2012-10-09 Tube Fabrication Design, Inc. Multiple cell heat transfer system
US9534818B2 (en) 2012-01-17 2017-01-03 Si2 Industries, Llc Heat pump system with auxiliary heat exchanger
US20180363278A1 (en) * 2012-10-09 2018-12-20 Philip Heller Humidity collector apparatus
US10683643B2 (en) * 2012-10-09 2020-06-16 Philip Heller Humidity collector apparatus
WO2017192612A1 (en) * 2016-05-02 2017-11-09 Wong Lee Wa Air conditioning and heat pump tower with energy efficient arrangement
US10612798B2 (en) 2016-05-02 2020-04-07 Lee Wa Wong Air conditioning and heat pump tower with energy efficient arrangement
US11021855B2 (en) * 2017-06-15 2021-06-01 Philip Heller Humidity collection apparatus

Also Published As

Publication number Publication date
DE1964530A1 (de) 1970-06-25
FR2027054A1 (ko) 1970-09-25
BE743606A (ko) 1970-05-28
GB1265229A (ko) 1972-03-01
DE1964530B2 (de) 1972-10-05

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