US3799243A - Liquid-vapor cycle air-condition system - Google Patents

Liquid-vapor cycle air-condition system Download PDF

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US3799243A
US3799243A US00312012A US31201272A US3799243A US 3799243 A US3799243 A US 3799243A US 00312012 A US00312012 A US 00312012A US 31201272 A US31201272 A US 31201272A US 3799243 A US3799243 A US 3799243A
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heat exchanger
air
enclosure
heat
pump
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H Castillo
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Eaton Corp
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Eaton Corp
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Priority to US00312012A priority Critical patent/US3799243A/en
Priority to DE2360088A priority patent/DE2360088A1/de
Priority to JP48136460A priority patent/JPS4996545A/ja
Priority to FR7343189A priority patent/FR2211629B3/fr
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Publication of US3799243A publication Critical patent/US3799243A/en
Priority to US47815374 priority patent/USRE28343E/en
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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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously

Definitions

  • references Cited UNITED STATES PATENTS 7/1970 Anderson 165/50 10/1964 Silvern 165/50 system having a turbine, a compressor and a liquid feed pump on a common shaft and a housing 'rotatably mounting this shaft and defining a liquid reservoir for the pump.
  • the system includes a reversing valve for switching between an air heating mode and an air cooling mode.
  • the heating mode -the coefficient of performance of the system is improved by recovering waste heat and water vapor from the exhaust gases produced by the flame.
  • the recovered water is also used to increase the humidity of the conditioned air.
  • a primary object of this invention is to provide a liquid-vapor cycle air conditioning system with an improved coefficient of performance.
  • a more specific object is to provide a reversible liquid-vapor cycle system having high performance coefficients in both the heating and cooling modes.
  • the invention air conditioning system is of the type including a heat exchanger in communication with the enclosure air, another heat exchanger in communication with air outside the enclosure, an expansion valve interposed between the heat exchangers, and a compressor interposed between the heat exchangers and driven by an energy transforming means, such as a turbine, receiving vapor from a vapor generator.
  • the vapor is generated by passing hot gases over the vapor generator, and at least a portion of thehot gases are thereafter directed to the heat exchanger in communication with the outside air whereby to improve the coefficient of performance of the system in the heating mode.
  • water condensate is collected from the hot gases as the latter are passed over the outside air heat exchanger and the condensate is then selectively introduced into the enclosure air to control the humidity in the enclosure.
  • the water condensate from the outside air heat exchanger is conducted to a third heat exchanger in the path of the hot gases, wherein it absorbs heat from the hot gases, and thence to a fourth heat exchanger in the path of the enclosure air, where it gives up heat to the enclosure air.
  • the system employs a single refrigerant type fluid for motive power production and air conditioning purposes, and the condensed fluid discharge from the energy transforming means and from the compressor is routed to a reversing valve which functions to selectively route this combined fluid discharge to the enclosure air heat exchanger, whereby to provide a heating operational mode for the system, or to the outside air heat exchanger, whereby to provide a cooling operational mode.
  • the water condensate formed on the enclosure air heat exchanger is collected and placed in communication with the outside air heat exchanger to improve the heat dissipation of the outside air heat exchanger.
  • the relative amounts of outside air and hot gases flowing over the outside air heat exchanger are modulated to thereby control the temperature of the gas mixture flowing over the outside air heat exchanger.
  • a pump on a common shaft with the turbine and compressor is provided between the enclosure air heat exchanger and the vapor generator to facilitate the return of condensed fluid to the generator, means are provided to sense an operational failure of the turbinecompressor-pump unit and establish an alternate fluid flow path between the enclosure air heat exchanger and the generator, thereby bypassing the shaft pump, and another pump is provided in the alternate fluid flow path which is energized in response to the sensed failure to provide an emergency heating mode operation for the system.
  • FIG. 1 is a perspective view of an air conditioning system according to the invention
  • FIG. 2 is a schematic view of the system of FIG. 1;
  • FIG. 3 is a diagram showing the refrigerant flow path when the system of FIG. 2 is operating in a cooling DESCRIPTION OF THE PREFERRED EMBODIMENT
  • various standard units are not shown in detail because they are individually well known in' the prior art.
  • Standard units employed in the present invention include heat exchangers, which may be of the well known fin and tube type, a boiler, blowers, valves electrically driven pumps, and spray nozzles.
  • control devices located within the enclosure to be conditioned, viz, a three-position heating-cooling switch, a thermostat, and a humidistat.
  • the function of these control devices is well known in the prior art.
  • the three-position heating-cooling switch has a heating position, an off position, and a cooling position. In the heating position, the switch operates various components in the system to condition the system to function in a heating mode. In the off position, the system is rendered inoperative. In the cooling position, the switch operates various components in the system which condition the system to function in a cooling mode.
  • the thermostat functions to automatically turn the system on or off in response to enclosure temperatures different than a desired enclosure temperature which is set into the thermostat.
  • the thermostat will complete a circuit to turn the system on in response to an enclosure temperature below the thermostat setting and will open the circuit to turn the system off in response to an enclosure temperature above the thermostat setting.
  • the thermostat functions in a reverse manner, i.e., the thermostat opens the circuit to turn the system off in response to enclosure temperature below the thermostat setting and closes the circuit to turn the system on in response to enclosure temperature above the thermostat setting.
  • the humidity of the enclosure air is below a predetermined amount the humidistat completes a circuit to various components in the system which function to add water to the enclosure air as it passes through the system.
  • the invention air conditioning system 10 is arranged to condition air in an enclosure 11.
  • system comprises a housing 12 divided by transverse partitions 14 and 16 into a lower compartment 18 housing a first heat exchanger 19 arranged to receive and condition enclosure air, a central compartment 20 housing the power source for the system and further housing a second heat exchanger 21 positioned in a central opening 22 in partition 16 for communication with air outside the enclosure, and an upper compartment 23 defining a buffer or safety zone to isolate the machinery in compartment 20 from the area outside housing 12.
  • lower compartment 18 contains a blower 24 for drawing air to be conditioned from enclosure 1 1 through a duct 26. Conditioned air is returned to enclosure 11 via a duct 28 after being blown over heat exchanger 19.
  • Compartment 18 further contains another heat exchanger 30 positioned within compartment 18 immediately upstream of heat exchanger 19. Water is supplied to heat exchanger 30 via a pipe 34 positioned within central compartment 20; water is drained from heat exchanger 30 via a pipe 36.
  • a water spray nozzle 38 directed toward heat exchangers 19, 30, is connected to pipe 34 via a valve 40. Valve 40, when open, allows water from pipe 34 to be sprayed over heat exchangers 19 and 30.
  • Valve 40 is controlled electrically in any well known manner by the humidistat located in enclosure 11.
  • a floor 41 positioned within compartment 18 is sloped toward a sump 42 which collects water from drain pipe 36 and condensate from heat exchanger 19.
  • a float switch 44 in the sump controls a pump 46 which pumps water from the sump upwardly through a pipe 48.
  • the power source for the system, housed within compartment 20, includes a vapor generator 50 and a turbo unit 52.
  • Vapor generator 50 comprises a boiler 54, a gas burner 56 disposed in heating relation beneath boiler 54, and a flue 58 arranged to direct the exhaust gases from burner 56 to atmosphere through upper compartment 23 and through a central opening 59 in top wall 60 of housing 12.
  • Turbo unit 52 comprises a turbine wheel 61, a compressor 62, and a liquid feed pump 64, all shown schematically.
  • Turbine wheel 61, compressor 62, and pump 64 are concentrically mounted on, and fixed to rotate with, a common shaft 66 which is journaled in a unitary, hermetically sealed turbo housing 68 having a pair of partitions 69, 70.
  • Partitions 69, 70 divide the interior of housing 68 into a compressor compartment 71, a
  • Pump compartment 73 houses pump 64 and provides a liquid receiver or reservoir for supplying the inlet of pump 64.
  • Shaft 66 may be journaled in housing 68 in any conventional manner, such as by gas bearings (not shown).
  • a pipe 74 interconnects the outlet of pump 64 and the inlet of boiler 54 and a pipe 76 interconnects the outlet of boiler 54 and the inlet of turbine wheel 61.
  • a check valve 78 is positioned in pipe 74 to prevent vapor backflow from boiler 54.
  • Compartment 20 also houses a reversing valve 80 and an expansion means or fluid throttling device 82.
  • a Y-shaped pipe having pipe portions 84, v and 86 interconnects an inlet of reversing valve 80 with the fluid discharge from turbine 61 and compressor 62.
  • a pipe 87 interconnects the inlet of compressor 62 with an outlet of valve 80.
  • a pipe 88 interconnects valve 80 and heat exchanger 19; a pipe 90 interconnects heat exchanger 19 and expansion means 82; a pipe 92 interconnects expansion means 82 and heat exchanger 21; a pipe 94 interconnects heat exchanger 21 and valve 80; a pipe 96 in parallel flow relationship with pipes 90 and 92 provides a bypass around expansion means 82; and a pipe 98 interconnects pipe 96 and receiver 73.
  • a pair of check valves 97, 99, at the ends of bypass pipe 96 allow fluid from either pipe 90 or 92 to flow into pipe 96 and prevent reverse flow.
  • Expansion means 82 may be a capillary restrictor tube or an expansion valve; both are well known in the art.
  • Valve 80 is a two-position, electrically controlled valve which is operated by the unshown heatingcooling switch located in enclosure 11; valve 85 may be of the general type disclosed in U.S. Pat. No. 3,003,334. When the heating and cooling switch is in the cooling position, valve 80 interconnects pipe 86 with pipe 94 and pipe 87 with pipe 88. When the heating and cooling switch is in the heating position valve 80 interconnects pipe 86 with pipe 88 and 87 with pipe 94.
  • Compartment 20 also houses an elbow-shaped duct 100 communicating at an end 101 with flue 58 and positioned at its other end 102 in opening 22 of partition 16.
  • Heat exchanger 21 is positioned within end 102 of duct 100.
  • a door valve 104 controlled by an electric motor 106, is positioned in duct end 101.
  • a blower 108 is positioned within duct 100 beneath heat exchanger 21.
  • a heat exchanger 109 positioned within duct 100 between valve 104 and blower 108, is connected at its inlet to pipe 48 and at its outlet to pipe 34.
  • the upper end of pipe 36 is connected to a water condensate sump defined by a low area in the downward sloping floor 110 of duct 100.
  • louvers 112 The right wall of duct 100 is provided with louvers 112 whose position may be varied by an electric motor 114.
  • a control circuit functions with the unshown enclosure heating-cooling switch in the cooling position to close door 104 and open louvers 112.
  • Another unshown control circuit including a thermostat 116 located in duct 100 between blower 108 and heat exchanger 21, functions with the enclosure heating-cooling switch in the heating position to synchronously control the positions of valve 104 and louvers 112.
  • Thermostat 1 16 functions to selectively modulate the position of valve 104 and louvers 112 when the system is in the heating mode to control the temperature of the air being blown over heat exchanger 21 by blower 108.
  • thermostat 116 may be set to maintain the air flowing over heat exchange 21 at approximately 100F.
  • a small amount of the exhaust gases from flue 58 will be required to boost the outside air flowing through louvers 112 to the required 100F.
  • valve 104 will be positioned to allow a small amount of exhaust gases from flue 58 to enter duct 100 while directing the remainder of the exhaust gases directly to atmosphere.
  • valve 104 opens more and louvers 1112 close more in response to thermostat 116, thereby maintaining the temperature of the air flowing over heat exchanger 21 at approximately 100F.
  • a water spray nozzle 118 is positioned within duct 100 between heat exchangers 21 and 109.
  • Nozzle 118 is connected to pipe 48 by a two-position solenoid valve 120 which, when energized, allows water communication between pipe 48 and nozzle 118 and blocks water communication between pipe 48 and heat exchanger 109 and, when deenergized, allows water communication between pipe 48 and heat exchanger 109 and blocks water communication between pipe 48 and nozzle 118. 7
  • Compartment also houses an apparatus for starting the system and for providing an emergency heating mode.
  • This starting and emergency heating apparatus comprises an electrically driven pump 128, a pipe 130 interconnecting pump 128 and receiver 73, a pipe 132 interconnecting pump 128 and pipe 74, a check valve 134 in pipe 130 which prevents reverse flow from pipe 74 when pump 128 is inoperative, and high and low temperature sensing switches 136, 138, respectively, arranged to sense the vapor discharge temperature in pipe 86.
  • the enclosure heating-cooling switch is moved to either the heating or cooling position. Assuming the enclosure temperature is below the setting of the enclosure thermostat with the heating-cooling switch in the heating position, or above the thermostat setting with the heating-cooling switch in the cooling position, an electrical circuit will be completed to the control valve for burner 56, whereby to light the burner, and to low temperature sensing switch 138.
  • the contacts of switch 138 are designed to close whenever the turbine discharge temperature is below a predetermined temperature, such as 100F. Since the system has been shut down, switch 138 will sense a temperature in pipe 86 below 100F. and its contacts will be closed to complete a circuit to pump 128.
  • Pump'l28 will thus be energized to draw liquid refrigerant from receiver 73 through pipe 130; the liquid refrigerant from pump 128 is delivered to vapor generator 50 through pipes 132 and 74.
  • the liquid refrigerant delivered to generator 50 is vaporized in boiler 54 by the heat from burner 56.
  • the refrigerant vapor is delivered to turbine 61 through pipe 76.
  • the refrigerant vapor drives turbine 61, and thereby compressor 62 and pump 64; refrigerant vapor discharge is delivered to pipe 86 where it heats switch 138 above 100F to cause the switch contacts to open and break the circuit to pump 128 which is thus deenergized.
  • the pumping action for the system is now assumed by pump 64 which delivers liquid refrigerant to vapor generator 59 from receiver 73 through pipe 74.
  • the described air conditioning system is capable of operating in three distinct modes, viz, a cooling mode, a heating mode, and an emergency mode.
  • the operation of the system in the cooling mode is shown schematically in the refrigerant flow diagram of FIG. 3.
  • valve is in its cooling mode position, i.e., pipes 86, 94 are interconnected and pipes 87, 88 are interconnected, and the thermostat in enclosure 11 will close its cooling contacts to complete a circuit for starting the system and maintaining the system in operation in response to enclosure air temperatures above the thermostat setting.
  • the vapor dis charge from turbine 61 and compressor 62 is conducted to heat exchanger 21 via pipe 86, valve 80, and pipe 94.
  • Heat exchanger 21 acts as a condenser; the vapor cools and liquifles as it flows through heat exchanger 21 by giving up heat to the outside air flowing over the heat exchanger.
  • a pipe 92 conducts the liquified refrigerant from heat exchanger 21 to check valve 99 and to expansion means 82.
  • a portion of the refrigerant flows through check valve 99 and returns to receiver 73 via pipes 96 and 98.
  • the other portion flows through expansion means 82 and undergoes a pressure and temperature drop.
  • the expanded refrigerant is conducted from the outlet of the expansion meansto heat exchanger 19 which acts as an evaporator; asthe refrigerant flows through heat exchanger 19, it vaporizes by absorbing heat from the enclosure air, thereby cooling the enclosure air.
  • the vaporized refrigerant leaving heat exchanger 19 is conducted to the compressor inlet via pipe 88, valve 80, and pipe 87.
  • blower 24 When activated, blower 24 facilitates movement of enclosure air over heat exchanger 19 and blower 108 facilitates movement of air over heat exchanger 21.
  • door 104 is closed in the cooling mode while louvers 112 are fully open so that the air being directed over exchanger 21 by blower 108 is comprised totally of ambient air flowing through louvers 49 and 112.
  • float switch 44 When water is available in sump 42, float switch 44 closes to complete a circuit to pump 46 and valve 120. Valve when activated interconnects pipe 48 with nozzle 118 and blocks connection of pipe 48 with heat exchanger 109. Pump 46 when activated pumps water from sump 42 to nozzle 1 18 which in turn sprays the water over heat exchanger 21, thereby wetting the outer surface of the heat exchanger and improving its heat dissipating capacity as the water evaporates.
  • This arrangement also serves to dispose of the water condensate which collects in sump 42 from heat exchanger 19. In an arid region water condensate from heat exchanger 19 may not be adequate for operation of the heat improving means; in this event sump 42 may be replenished by the enclosure water system.
  • valve 80 is in its heating mode position, i.e., pipes 86, 88 are interconnected and pipes 87, 94 are interconnected, and the enclosure thermostat will close its heating contacts to complete a circuit for starting and maintaining the system in operation in re sponse to enclosure air temperatures below the thermostat setting.
  • refrigerant flow through heat exchangers 19, 21 and expansion means 82 is reversed with respect to refrigerant flow in the cooling mode.
  • Heat exchanger 19 now acts as a condenser; the vapor cools and liquifies as it flows through the exchanger by giving up heat to the enclosure air flowing over the exchanger, whereby to heat the enclosure air.
  • Pipe 90 conducts the liquid refrigerant discharge from heat exchanger 19 to check valve 97 and to expansion means 82. A portion of the liquid refrigerant flows through check valve 97 for return to receiver 73 via pipes 96 and 98. The other portion flows through expansion means 82 and undergoes a pressure and temperature drop.
  • the expanded refrigerant is conducted from the outlet of the expansion means to heat exchanger 21 which now acts as an evaporator; as the refrigerant flows through exchanger 21, it vaporizes and absorbs heat from the outside air flowing over it.
  • the vaporized refrigerant leaving heat exchanger 21 is conducted to the compressor inlet via pipe 94, valve 80, and pipe 87.
  • blower 24 When activated, as in the cooling mode, blower 24 facilitates movement of enclosure air over heat exchanger 19, and blower 108 facilitates movement of air over heat exchanger 21.
  • closure of the heating contacts further activates meansfor improving the system coefficient of performance.
  • thermostat 116 and its associated control circuit are activated to selectively modulate the synchronous operation of door valve 104 and louvers 112 to maintain the air flowing over heat exchanger 21 at approximately lOOF, thereby improving the systems coefficient of performance by using waste heat from the exhaust gases.
  • thermostat 116 will function to open door 104 a substantial amount while substantially closing louvers l 12, thereby mixing a large volume exhaust gases from flue 58 with the relatively small volume of cold outside air flowing through the louvers 112 to produce a lF air flow over heat exchanger 21.
  • the coefficient of performance of the system in the heating mode is further improved by providing apparatus for optimizing the amount of heat extracted from the exhaust gases.
  • This apparatus comprises heat exchangers 30, 109, pump 46, and interconnecting pipes and controls. Since heat exchanger 21 acts as an evaporator during the heating mode, condensate will be precipitated from moisture laden air flowing over its outer surface. This condensate is communicated to sump 42 via pipe 36. With the heating-cooling switch in the heating position and the heating contacts of the enclosure thermostat closed, an electric circuit is completed to float switch 44. Float switch 44 completes a circuit to activate pump 46 if water is available in sump 42. Pump 46, when activated, pumps water from sump 42 through heat exchanger 109 via pipe 48 and deenergized valve 120.
  • the water is returned to sump 42 via pipe 34 and heat exchanger 30.
  • the water flowing through heat exchanger 109 absorbs heat from the exhaust gases flowing over its outer surface, thereby precooling the exhaust gases flowing over the heat exchanger 21 and allowing greater volumes of the exhaust gases to be used for this purpose.
  • the heated water from heat exchanger 109 then flows to heat exchanger 30 where it rejects heat to the enclosure air circulating toward heat exchanger 19.
  • Means are also provided for improving the humidity of the conditioned air while operating in the heating mode.
  • the enclosure humidistat is operable in response to sensing a low humidity condition to complete a circuit to open valve 40, thereby allowing water from pipe 34 to be sprayed over heat exchangers 19, 30 by nozzle 38.
  • the disclosed air conditioning system also embodies provision for operation in an emergency heating mode in the event of failure of turbo unit 52.
  • the operation of the system in the emergency mode is shown schematically in the refrigerant flow diagram of FIG. 5; With the system operating in the heating mode, the emergency mode is automatically switched on when switch 136 senses a turbine vapor discharge temperature exceeding a predetermined value, such as 250F; this excess temperature, which is indicative of failure of turbo unit 52, causes switch 136 to close its contacts to complete an electrical circuit to energize pump 128.
  • Pump 128, when energized by switch 136 provides liquid refrigerant from receiver 73 to boiler 54 to maintain the system in operation.
  • turbo unit 52 hot refrigerant vapor from boiler 54 flows through pipe 76, disabled turbine 61, pipe 86, valve 80, pipe 88, heat exchanger 19, pipe 90, check valve 97, pipes 96, 98, receiver 73, pipe 30, pump 128, check valve 134, and pipes 132, 74.
  • the heating capacity of the system is diminished, but is effective enough to provide heat to the enclosure until repairs can be made on the turbo unit.
  • heat exchanger 21 and expansion means 82 are in effect bypassed. It will be understood that failure of turbo unit 52 may consist, for example, of seizure of shaft 66 or disintegration of turbine or compressor blading.
  • a liquid-vapor cycle air conditioning system for maintaining the air of an enclosure in a predetermined condition, said system comprising:
  • C. means directing hot gases to said vapor generator to vaporize said liquid
  • D. means receiving vapor from said generator and operative to transform heat energy of said vapor to mechanical energy
  • G means directing enclosure air to said first heat exchanger
  • expansion means receiving discharge fluid from said first heat exchanger
  • J. means directing outside air to said second heat exchanger
  • K means directing discharge fluid from said second heat exchanger to said compressor
  • L means for directing at least a portion of said hot gases into a heat exchange relation with said second heat exchanger.
  • M means for collecting water condensate from said hot gases in said heat exchange relation with said second heat exchanger
  • N means for introducing said condensate to said enclosure air.
  • the fluid conducted to said third and fourth heat exchanger is water
  • said system further includes means for selectively admitting at least a portion of said water to said enclosure air, thereby improving the humidity of said enclosure air.
  • a liquid-vapor cycle air conditioning system for maintaining the air of an enclosure in a predetermined condition, said system comprising:
  • C. means receiving a vapor from said generator and operative to transform the heat energy of said vapor to mechanical energy
  • expansion means interconnecting said first and second heat exchanger
  • valve means interposed between said first and second heat exchangers and selectively movable between v 1. a first position in which discharge fluid from saidenergy transforming means and said compressor is directed to said first heat exchanger and from said first heat exchange to said expansion means, thence to said second heat exchanger, and thence to the inlet of said compressor, and
  • J. means for placing said water condensate in communication with said second heat exchanger, thereby improvingthe heat dissipation of said second heat exchanger.
  • said transforming means comprises a turbine on a common shaft with said compressor
  • said supplying means is mounted on and driven by said shaft.
  • K a unitary, hermetically sealed housing having said common shaft journaled therein;
  • L. means in said housing defining a fluid reservoir receiving a portion of the outlet fluid from said first heat exchanger and supplying the inlet of said pump.
  • said pump is positioned within said reservoir.
  • M means for sensing an operational failure of the turbine-compressor-pump unit and operative in response to such sensed failure to establishanalternate fluid flow path from said first heat exchanger to said generator bypassing said pump;
  • said second pump is connected at its inlet to said reservoir.
  • sensing means operable to energize said second pump in response to sensing an inoperative condition of said system and an enclosure air-.
  • N.'sa id sensing means for sensing said inoperative condition and said enclosure air-condition includes, respectively, l. switch means responsive to the fluid discharge temperature of said turbine and compressor, and
  • a liquid-vapor cycle air conditioning system for maintaining the air of an enclosure in a predetermined condition, said system comprising:
  • F. means directing the combined fluid discharge of said turbine and compressor to said first heat exchanger and then a portion of the discharge fluid of said first heat exchanger to the inlet of said pump and the other portion to said expansion means, then to said second heat exchanger, and then to the inlet of said compressor.
  • a system according to claim 15 further including:
  • G means for controlling the temperature of the outside air in heat exchange relation with said second heat exchanger.
  • said vapor is generated by flowing hot gases over said vapor generator
  • said temperature controlling means includes synchronously controlled valve means selectively operative to direct varying portions of said hot gases and said outside air into heat exchange relation with said second heat exchanger.
  • said vapor generator includes a fuel combusting device for producing said hot gases.
  • K means for collecting water condensate from said gases in said heat exchange relation with said second heat exchanger
  • L means for introducing said condensate to said enclosure air.
  • V N the fluid conducted to said third and fourth heat exchanger is water
  • said system further includes means for selectively admitting at least a portion of said water to said enclosure air, thereby improving the humidity of said enclosure air. 22.
  • valve means selectively movable between 1. a first position in which the fluid flows in accordance with claim 15, and 2. a second position in which said combined discharge fluid is routed to flow to said second heat exchanger and from said second heat exchanger 25 a. in part to the inlet of said pump, and
  • T means for placing said water condensate in communication with said second heat exchanger
  • said directing means includes:
  • valve means selectively movable between 1. a first position in which the fluid flows in accordance with claim 15, and
  • a second one-way check valve for preventing fluid flow from said pump inlet to said first heat exchanger when said valve means-is in said second position.
  • G means for sensing an operational failure of said turbo unit and operative in response to such sensed failure to establish an alternate fluid flow path from said first heat exchanger to the inlet of said vapor generator bypassing said pump;
  • sensing means includes:
  • G means for providing starting fluid to said vapor generator, said means comprising 1. a second pump for supplying fluid to the inlet of said vapor generator, and
  • sensing means operable to energize said second pump in response to sensing an inoperative condition of said turbo unit and an enclosure air temperature different than said predetermined condition.
  • a system according to claim 28, wherein said means sensing an inoperative condition of said turbo unit includes:
  • H means for sensing the fluid discharge temperature of said turbine and operable in response to discharge temperatures below a predetermined amount.
  • a liquid-vapor cycle air conditioning system for maintaining the air of an enclosure in a predetermined condition, said system comprising:
  • a turbo unit having 1. a hermetically sealed housing, 2. a shaft journaled in said housing,
  • expansion means interconnected between said first and second heat exchangers
  • F. means operative to selectively switch said system heat exchangers is disposed in heat exchange relation with the air outside said enclosure and.said combined discharge is directed to that heat exchanger and the discharge from the other heat exchanger is directed to the inlet of said compressor;
  • G means operative in either operational mode to direct a portion of the discharge from the heat exchanger receiving said combined discharge to said reservoir and the remaining portion to said expansion means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
US00312012A 1972-12-04 1972-12-04 Liquid-vapor cycle air-condition system Expired - Lifetime US3799243A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US00312012A US3799243A (en) 1972-12-04 1972-12-04 Liquid-vapor cycle air-condition system
DE2360088A DE2360088A1 (de) 1972-12-04 1973-12-03 Vorrichtung zum klimatisieren mit fluessigkeits-dampf-zyklus
JP48136460A JPS4996545A (de) 1972-12-04 1973-12-04
FR7343189A FR2211629B3 (de) 1972-12-04 1973-12-04
US47815374 USRE28343E (en) 1972-12-04 1974-06-27 Liquid-vapor cycle air-conditiom system

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US00312012A US3799243A (en) 1972-12-04 1972-12-04 Liquid-vapor cycle air-condition system

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JP (1) JPS4996545A (de)
DE (1) DE2360088A1 (de)
FR (1) FR2211629B3 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5003788A (en) * 1989-09-05 1991-04-02 Gas Research Institute Gas engine driven heat pump system
US5216899A (en) * 1990-11-29 1993-06-08 Gracio Fabris Rotating single cycle two-phase thermally activated heat pump
US5236349A (en) * 1990-10-23 1993-08-17 Gracio Fabris Two-phase reaction turbine
US6220341B1 (en) * 1997-11-19 2001-04-24 Sanyo Electric Co., Ltd. Air conditioning system
US20160325657A1 (en) * 2013-12-31 2016-11-10 Gentherm Automotive Systems (China) Ltd. Ventilation system

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2457468A1 (fr) * 1979-05-23 1980-12-19 Creusot Loire Installation de transfert de chaleur
JP5220334B2 (ja) * 2007-04-04 2013-06-26 三菱電機株式会社 貯湯式給湯機

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3153442A (en) * 1961-06-26 1964-10-20 David H Silvern Heating and air conditioning apparatus
US3519066A (en) * 1968-02-05 1970-07-07 James H Anderson Heat pump

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3259176A (en) * 1963-07-09 1966-07-05 United Aircraft Corp Environmental control system

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3153442A (en) * 1961-06-26 1964-10-20 David H Silvern Heating and air conditioning apparatus
US3519066A (en) * 1968-02-05 1970-07-07 James H Anderson Heat pump

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5003788A (en) * 1989-09-05 1991-04-02 Gas Research Institute Gas engine driven heat pump system
US5236349A (en) * 1990-10-23 1993-08-17 Gracio Fabris Two-phase reaction turbine
US5216899A (en) * 1990-11-29 1993-06-08 Gracio Fabris Rotating single cycle two-phase thermally activated heat pump
US6220341B1 (en) * 1997-11-19 2001-04-24 Sanyo Electric Co., Ltd. Air conditioning system
US20160325657A1 (en) * 2013-12-31 2016-11-10 Gentherm Automotive Systems (China) Ltd. Ventilation system

Also Published As

Publication number Publication date
FR2211629A1 (de) 1974-07-19
JPS4996545A (de) 1974-09-12
DE2360088A1 (de) 1974-06-12
FR2211629B3 (de) 1976-10-15

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