Abstract:
A method for controlling a refrigerant path apparatus including a pressurized gas refrigerant path for a flow of a pressurized gas refrigerant which has not been substantially cooled to be liquefied, a pressurized liquid refrigerant path for a flow of a pressurized liquid refrigerant which is generated from the pressurized gas refrigerant by being cooled to be liquefied, a first heat exchanger means which is fluidly connected to the pressurized gas refrigerant path to supply the pressurized gas refrigerant into the first heat exchanger so that a heat exchange is carried out between the pressurized gas refrigerant in the first heat exchanger and the outside of the first heat exchanger, comprises the steps of allowing a flow of the refrigerant from the pressurized gas refrigerant path to the pressurized liquid refrigerant path when a supply of the pressurized gas refrigerant from the pressurized gas refrigerant path into the first heat exchanger means is prevented, and preventing the flow of the refrigerant from the pressurized gas refrigerant path to the pressurized liquid refrigerant path when the supply of the pressurized gas refrigerant form the pressurized gas refrigerant path into the first heat exchanger means is allowed.

Description:
BACKGROUND OF THE INVENTION AND RELATED ART STATEMENT 
     The present invention relates to a refrigerant path apparatus used in a air-conditioning system. 
     As shown in Japanese Patent Unexamined Publication No. 2-223776, a conventional heat pump system for warming or cooling an air in a room to be air-conditioned, comprises a compressor which takes in a refrigerant through an inlet thereof and discharges the refrigerant through an outlet thereof after the refrigerant is compressed, an adiabatic expansion orifice which includes first and second orifice ends and through which the compressed refrigerant expands adiabatically, a first heat exchanger whose first end is fluidly connected to the outlet of the compressor on a cooling operation for the air-conditioned room and to the inlet of the compressor on a warming operation for the air-conditioned room and whose second end is fluidly connected to the first orifice end, and a second heat exchanger whose first end is fluidly connected to the second orifice end and whose second end is fluidly connected to the inlet of the compressor on the cooling operation and to the outlet of the compressor on the warming operation. 
     OBJECT AND SUMMARY OF THE INVENTION 
     An object of the present invention is to provide a refrigerant path apparatus which is used in an air-conditioning system and in which an unnecessary liquefying of the refrigerant is prevented. 
     A refrigerant path apparatus according to the present invention, comprises, 
     a pressurized gas refrigerant path for a flow of a pressurized gas refrigerant which has not been substantially cooled to be liquefied after the gas of the refrigerant was compressed to be pressurized, 
     a pressurized liquid refrigerant path for a flow of a pressurized liquid refrigerant which has been substantially cooled to be liquefied after the gas of the refrigerant was compressed to be pressurized, 
     a first heat exchanger mans which is fluidly connected to the pressurized gas refrigerant path to supply the pressurized gas refrigerant into the first heat exchanger so that a heat exchange is carried out between the pressurized gas refrigerant in the first heat exchanger and the outside of the first heat exchanger, 
     a first valve means arranged between the first heat exchanger means and the pressurized gas refrigerant path to control the supply of the pressurized gas refrigerant into the first heat exchanger mans, and 
     a second valve means arranged between the pressurized gas refrigerant path and the pressurized liquid refrigerant path to allow a flow of the refrigerant from the pressurized gas refrigerant path to the pressurized liquid refrigerant path when the first valve means prevents the supply of the pressurized gas refrigerant from the pressurized gas refrigerant path into the first heat exchanger mans. 
     A method for controlling a refrigerant path apparatus including a pressurized gas refrigerant path for a flow of a pressurized gas refrigerant which has not been substantially cooled to be liquefied after the gas of the refrigerant was compressed to be pressurized, a pressurized liquid refrigerant path for a flow of a pressurized liquid refrigerant which has been substantially cooled to be liquefied after the gas of the refrigerant was compressed to be pressurized, and a first heat exchanger means which is fluidly connected to the pressurized gas refrigerant path to supply the pressurized gas refrigerant into the first heat exchanger so that a heat exchange is carried out between the pressurized gas refrigerant in the first heat exchanger and the outside of the first heat exchanger, comprises the steps of 
     allowing a flow of the refrigerant from the pressurized gas refrigerant path to the pressurized liquid refrigerant path when a supply of the pressurized gas refrigerant from the pressurized gas refrigerant path into the first heat exchanger means is prevented, and 
     preventing the flow of the refrigerant from the pressurized gas refrigerant path to the pressurized liquid refrigerant path when the supply of the pressurized gas refrigerant from the pressurized gas refrigerant path into the first heat exchanger means is allowed. 
     According to the present invention, since the flow of the refrigerant from the pressurized gas refrigerant path to the pressurized liquid refrigerant path is allowed when the supply of the pressurized gas refrigerant from the pressurized gas refrigerant path into the first heat exchanger means is prevented, the flow of the refrigerant in the pressurized gas refrigerant path is maintained to prevent the refrigerant in the pressurized gas refrigerant path from being cooled to be liquefied. Since a flow rate for preventing the refrigerant in the pressurized gas refrigerant path from being liquefied may be small, the flow of the refrigerant from the pressurized gas refrigerant path to the pressurized liquid refrigerant path does not generate a significant problem. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a schematic view showing an embodiment of the present invention. 
     FIG. 2 is a schematic view showing an embodiment of the present invention. 
     FIG. 3 is a schematic view showing an embodiment of the present invention. 
     FIG. 4 is a schematic view showing an embodiment of the present invention. 
     FIG. 5 is a schematic view showing an embodiment of the present invention. 
     FIG. 6 is a schematic view showing an embodiment of the present invention. 
     FIG. 7 is a schematic view showing an embodiment of the present invention. 
     FIG. 8 is a schematic view showing an embodiment of the present invention. 
     FIG. 9 is a schematic view showing an embodiment of the present invention. 
     FIG. 10 is a schematic view showing an embodiment of the present invention. 
    
    
     DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS 
     As shown in FIG. 1, in an embodiment of the present invention, a pressurized gas refrigerant which has not been substantially cooled by any of first heat exchangers 5a and 5b and second heat exchangers 10a and 10b after the pressurized gas refrigerant was discharged from an outlet of a compressor 3 is supplied to a pressurized gas refrigerant path 15, a pressurized liquid refrigerant which is generated by cooling the pressurized gas refrigerant to be liquefied in any of the first heat exchangers 5a and 5b and the second heat exchangers 10a and 10b is supplied to a pressurized liquid refrigerant path 17, a depressurized gas refrigerant which is generated by making the pressurized liquid refrigerant pass through any of adiabatic expansion orifices 6a, 6b, 9a, 9b for an adiabatic expansion of the pressurized liquid refrigerant, and a depressurized heated gas refrigerant which is generated by heating the depressurized gas refrigerant in any of the first heat exchangers 5a and 5b and the second heat exchangers 10a and 10b is supplied to a depressurized heated gas refrigerant path 16. Any of the first heat exchangers 5a and 5b may be used as an indoor heat exchanger or an outdoor heat exchanger, and any of the second heat exchangers 10a and 10b may be used as the indoor heat exchanger or the outdoor heat exchanger. 
     Preferably, the first heat exchangers 5a and 5b are used as the outdoor heat exchanger, and the second heat exchangers 10a and 10b are used as the indoor heat exchanger, when the first heat exchangers 5a and 5b and the compressor 3 are received by an outdoor unit 1 accommodating the adiabatic expansion orifices 6a, 6b, a fan 25 for accelerating a heat exchange between the refrigerant in the first heat exchangers 5a and 5b and the outside thereof, a receiver 7 arranged between the adiabatic expansion orifices 6a, 6b and the adiabatic expansion orifices 9a, 9b for storing the pressurized liquid refrigerant, an adiabatic expansion bypass valve 13 which opens slightly to allow a significantly small flow of the pressurized liquid refrigerant from the pressurized liquid refrigerant path 17 to an inlet of the compressor 3 when the compressor 3 needs to be cooled by the depressurized gas refrigerant generated through the adiabatic expansion bypass valve 13, an accumulator 8 fluidly connected to the inlet of the compressor 3 for storing the depressurized heated gas refrigerant to be taken from the depressurized heated gas refrigerant path 16 into the inlet of the compressor 3, four-ports two-positions flow direction control valves 4a, 4b connected fluidly to the first heat exchangers 5a and 5b respectively, in whose one position the pressurized gas refrigerant is supplied from the outlet of the compressor 3 to the respective first heat exchangers 5a and 5b and the depressurized heated gas refrigerant is supplied from the depressurized heated gas refrigerant path 16 to the inlet of the compressor 3 and in whose another position the pressurized gas refrigerant is supplied from the outlet of the compressor 3 to the pressurized gas refrigerant path 15 and the depressurized heated gas refrigerant is supplied from the respective first heat exchangers 5a and 5b to the inlet of the compressor 3, and an one-way valve 14 for preventing a pressurized gas refrigerant flow from the pressurized gas refrigerant path 15 to the flow direction control valves 4b and allowing the pressurized gas refrigerant flow from the flow direction control valves 4b to the pressurized gas refrigerant path 15. When the control valves 4a, 4b form respective fluidal connections as shown by solid lines in FIG. 1, the orifice 6a is closed to prevent a refrigerant flow from the first heat exchanger 5a to the control valve 4a. 
     When any of the first heat exchangers 5a and 5b operates to heat the depressurized gas refrigerant and any of the second heat exchangers 10a and 10b operates to cool the pressurized gas refrigerant to supply the pressurized liquid refrigerant to the any of the adiabatic expansion orifices 6a, 6b, 9a, 9b, any of the adiabatic expansion orifices 6a, 6b fluidly connected to the any of the first heat exchangers 5a and 5b operating to heat the depressurized gas refrigerant opens slightly to effect an adiabatic expansion and any of the adiabatic expansion orifices 9a, 9b fluidly connected to the any of the second heat exchangers 10a and 10b operating to cool the pressurized gas refrigerant opens largely not to form a large flow resistance. When any of the first heat exchangers 5a and 5b operates to cool the pressurized gas refrigerant to supply the pressurized liquid refrigerant to the any of the adiabatic expansion orifices 6a, 6b, 9 a, 9b and any of the second heat exchangers 10a and 10b operates to heat the depressurized gas refrigerant, any of the adiabatic expansion orifices 6a, 6b fluidly connected to the any of the first heat exchangers 5a and 5b operating to cool the pressurized gas refrigerant opens largely not to form the large flow resistance and any of the adiabatic expansion orifices 9a, 9b fluidly connected to the any of the second heat exchangers 10a and 10b operating to heat the depressurized gas refrigerant opens slightly to effect the adiabatic expansion. Therefore, the pressurized liquid refrigerant always exists at least between the adiabatic expansion orifices 6a, 6b and the adiabatic expansion orifices 9a, 9b. 
     An indoor unit 2a accommodates the second heat exchanger 10a, the adiabatic expansion orifice 9a and a fan 25 for accelerating a heat exchange between the refrigerant in the second heat exchanger 10a and the outside thereof. An indoor unit 2b accommodates the second heat exchanger 10b, the adiabatic expansion orifice 9b and a fan 25 for accelerating a heat exchange between the refrigerant in the second heat exchanger 10b and the outside thereof. 
     The pressurized liquid refrigerant path 17 is connected to one end of the second heat exchanger 10a through the adiabatic expansion orifice 9a and a pressurized liquid refrigerant path branch 23a, the depressurized heated gas refrigerant path 16 is connected to another end of the second heat exchanger 10a through a depressurized heated gas refrigerant path branch 22a and a third valve 12a, and the pressurized gas refrigerant path 15 is connected to the another end of the second heat exchanger 10a through a pressurized gas refrigerant path branch 21a and a first valve 11a. The pressurized gas refrigerant path branch 21a is connected to the pressurized liquid refrigerant path branch 23a by a bypass 24a and a second valve 18a which can allow a slight flow of the refrigerant from the pressurized gas refrigerant path branch 21a to the pressurized liquid refrigerant path branch 23a through the bypass 24a when the first valve 11a prevents the refrigerant from flowing from the pressurized gas refrigerant path 15 to the second heat exchanger 10a. 
     When the second heat exchanger 10a operates to cool the outside thereof, the first valve 11a is closed to prevent the pressurized gas refrigerant from flowing from the pressurized gas refrigerant path 15 to the second heat exchanger 10a, the third valve 12a opens to allow the depressurized heated refrigerant to flow from the second heat exchanger 10a to the depressurized heated gas refrigerant path branch 22a, and the adiabatic expansion orifice 9a opens slightly to generate the depressurized gas refrigerant from the pressurized liquid refrigerant for cooling the outside of the second heat exchanger 10a. If there is a possibility that the pressurized gas refrigerant in the pressurized gas refrigerant path 15 and/or the pressurized gas refrigerant path branch 21a is cooled to be liquefied, or if a change from the pressurized gas refrigerant to the pressurized liquid refrigerant is detected in the pressurized gas refrigerant path 15 and/or the pressurized gas refrigerant path branch 21a, the second valve 18a allows the slight flow of the refrigerant from the pressurized gas refrigerant path branch 21a to the pressurized liquid refrigerant path branch 23a so that the refrigerant in the pressurized gas refrigerant path branch 21a and/or the pressurized gas refrigerant path 15 can be heated by the pressurized gas refrigerant supplied from the compressor 3 to prevent the liquefying of the refrigerant in the pressurized gas refrigerant path branch 21a and/or the pressurized gas refrigerant path 15. 
     When the second heat exchanger 10a operates to heat the outside thereof, the first valve 11a is opened to allow the pressurized gas refrigerant from flowing from the pressurized gas refrigerant path 15 to the second heat exchanger 10a, the third valve 12a is closed to prevent the refrigerant from flowing from the second heat exchanger 10a to the depressurized heated gas refrigerant path branch 22a, and the adiabatic expansion orifice 9a opens largely not to form the large refrigerant flow resistance from the second heat exchanger 10a to the pressurized liquid refrigerant path branch 23a. Since a pressure in the depressurized heated gas refrigerant path 16 and the depressurized heated gas refrigerant path branch 22a is low, the refrigerant therein the vaporized to prevent the liquefying of the refrigerant therein. 
     When the second heat exchanger 10a stops to heat or cool the outside thereof, the first valve a is closed to prevent the pressurized gas refrigerant from flowing from the pressurized gas refrigerant path 15 to the second heat exchanger 10a, the third valve 12a opens to allow the refrigerant to flow from the second heat exchanger 10a to the depressurized heated gas refrigerant path branch 22a, and the adiabatic expansion orifice 9a is closed to prevent the refrigerant from flowing between the second heat exchanger 10a and the pressurized liquid refrigerant path branch 23a. If there is a possibility that the pressurized gas refrigerant in the pressurized gas refrigerant path 15 and/or the pressurized gas refrigerant path branch 21a is cooled to be liquefied, or if a change from the pressurized gas refrigerant to the pressurized liquid refrigerant is detected in the pressurized gas refrigerant path 15 and/or the pressurized gas refrigerant path branch 21a, the second valve 18a allows the slight flow of the refrigerant from the pressurized gas refrigerant path branch 21a to the pressurized liquid refrigerant path branch 23a so that the refrigerant in the pressurized gas refrigerant path branch 21a and/or the pressurized gas refrigerant path 15 can be heated by the pressurized gas refrigerant supplied from the compressor 3 to prevent the liquefying of the refrigerant in the pressurized gas refrigerant path branch 21a and/or the pressurized gas refrigerant path 15. Since the third valve 12a is opening, the refrigerant in the second heat exchanger 10a is vaporized by a pressure in the depressurized heated gas refrigerant path 16 to prevent the liquefying of the refrigerant in the depressurized heated gas refrigerant path 16, the depressurized heated gas refrigerant path branch 22a and the second heat exchanger 10a. The second valve 18a may be directly connected to the pressurized liquid refrigerant path 17 with deletion of the bypass 24a. 
     Generally, in heat pump systems, a pressure Pd in the pressurized gas refrigerant path 15 is slightly higher than a pressure P1 in the pressurized liquid refrigerant path 17, and the pressure P1 in the pressurized liquid refrigerant path 17 is significantly higher than a pressure Ps in the depressurized heated gas refrigerant path 16. 
     The pressurized liquid refrigerant path 17 is connected to one end of the second heat exchanger 10b through the adiabatic expansion orifice 9b and a pressurized liquid refrigerant path branch 23b, the depressurized heated gas refrigerant path 16 is connected to another end of the second heat exchanger 10b through a depressurized heated gas refrigerant path branch 22b and a third valve 12b, and the pressurized gas refrigerant path 15 is connected to the another end of the second heat exchanger 10b through a pressurized gas refrigerant path branch 21b and a first valve 11b. The pressurized gas refrigerant path branch 21b is connected to the pressurized liquid refrigerant path branch 23b by a bypass 24b and a second valve 18b which can allow a slight flow of the refrigerant from the pressurized gas refrigerant path branch 21b to the pressurized liquid refrigerant path branch 23b through the bypass 24b when the first valve 11b prevents the refrigerant from flowing from the pressurized gas refrigerant path 15 to the second heat exchanger 10b. Operations of the second heat exchanger 10b, the adiabatic expansion orifice 9b, the third valve 12b, the second valve 18b and the first valve 11b are controlled respectively in the same ways as the second heat exchanger 10a, the adiabatic expansion orifice 9a, the third valve 12a, the second valve 18a and the first valve 11a. 
     As shown in FIG. 2, an one-way flow valve 19a may be arranged between the pressurized gas refrigerant path branch 21a and the pressurized liquid refrigerant path branch 23a to prevent a refrigerant flow from the pressurized liquid refrigerant path branch 23a to the pressurized gas refrigerant path branch 21a and to allow a refrigerant flow from the pressurized gas refrigerant path branch 21a to the pressurized liquid refrigerant path branch 23a. Alternatively, a pump 19a for feeding compulsorily the refrigerant from the pressurized gas refrigerant path branch 21a to the pressurized liquid refrigerant path branch 23a and preventing the refrigerant flow from the pressurized liquid refrigerant path branch 23a to the pressurized gas refrigerant path branch 21a may be arranged between the pressurized gas refrigerant path branch 21a and the pressurized liquid refrigerant path branch 23a. 
     As shown in FIG. 3, a heat exchange between the refrigerant in the bypass 24a and the refrigerant in the depressurized heated gas refrigerant path branch 22a may be carried out in a heat exchanger 20a so that the gas refrigerant flowing from the pressurized gas refrigerant path branch 21a to the pressurized liquid refrigerant path branch 23a through the bypass 24a can be liquefied by a low temperature of the refrigerant in the depressurized heated gas refrigerant path branch 22a. 
     As shown in FIG. 4, the second valve 18a may be controlled by a controller 30 according to the operation of the first valve 11a so that the second valve 18a is opened when a predetermined time has been elapsed after the refrigerant flow from the pressurized gas refrigerant path branch 21a into the second heat exchanger 10a had been cut off by the first valve 11a. 
     As shown in FIG. 5, the second valve 18a may be controlled by the controller 30 according to the condition of the refrigerant in the pressurized gas refrigerant path branch 21a and/or the pressurized gas refrigerant path 15. The condition of the refrigerant in the pressurized gas refrigerant path branch 21a and/or the pressurized gas refrigerant path 15 is detected by a sensor 31 which can measure a decrease in temperature of the refrigerant in the pressurized gas refrigerant path branch 21a and/or the pressurized gas refrigerant path 15 or a generated value of the liquefied refrigerant in the pressurized gas refrigerant path branch 21a and/or the pressurized gas refrigerant path 15. When the measured temperature of the refrigerant reaches less than a predetermined temperature sufficient for liquefying the gas refrigerant, or when the measured value of the liquefied refrigerant reaches more than a predetermined value, the second valve 18a is opened. The sensor 31 may be a temperature sensor or a capacitance type level gauge. 
     In an embodiment as shown in FIG. 6, the refrigerant in the pressurized gas refrigerant path 15 flows into the pressurized liquid refrigerant path 17 without passing through the pressurized liquid refrigerant path branches 23a, 23b, 23c, when any of the first valves 11a, 11b, 11c is closed so that the refrigerant flow from the pressurized gas refrigerant path 15 to any of the second heat exchangers 10a, 10b, 10c is cut off. 
     In an embodiment as shown in FIG. 7, since a time in which the pressurized liquid refrigerant is supplied from the second heat exchanger 10b to the pressurized liquid refrigerant path 17 or supplied from the pressurized liquid refrigerant path 17 to the adiabatic expansion orifice 9b is significantly larger than a time in which the pressurized liquid refrigerant is supplied from the second heat exchanger 10a or 10c to the pressurized liquid refrigerant path 17 or supplied from the pressurized liquid refrigerant path 17 to the adiabatic expansion orifice 9a or 9c, the refrigerant in the pressurized gas refrigerant path 15 flows into the pressurized liquid refrigerant path 17 adjacently to the second heat exchanger 10b when the first valve 11a or 11c is closed. 
     In an embodiment as shown in FIG. 8, since a time in which the pressurized liquid refrigerant is supplied from the pressurized liquid refrigerant path 17 to the adiabatic expansion orifice 9c connected to the second heat exchanger 10c used only to heat the depressurized gas refrigerant is significantly larger than a time in which the pressurized liquid refrigerant is supplied from the second heat exchanger 10a or 10b to the pressurized liquid refrigerant path 17 or supplied from the pressurized liquid refrigerant path 17 to the adiabatic expansion orifice 9a or 9b, the refrigerant in the pressurized gas refrigerant path 15 flows into the pressurized liquid refrigerant path 17 adjacently to the second heat exchanger 10c when the first valve 11a or 11b is closed. 
     In an embodiment as shown in FIG. 9, valves 22a, 22b, 22c are arranged between the pressurized liquid refrigerant path 17 and the second valves 18a, 18b, 18c. Any of the valves 22a, 22b, 22c connected to the pressurized liquid refrigerant path 17 adjacently to any of the second heat exchanger 10a, 10b, 10c which is operating to heat or cool the refrigerant is opened so that the refrigerant in the pressurized gas refrigerant path 15 flows into the pressurized liquid refrigerant path 17 adjacently to the second heat exchanger 10c when the first valve 11a or 11b or 11c is closed. However, any of the valves 22a, 22b, 22c connected to the pressurized liquid refrigerant path 17 adjacently to any of the second heat exchanger 10a, 10b, 10c which is not operating is closed. 
     In an embodiment as shown in FIG. 10, the second valves 18a, 18b is connected to the receiver 7 through an one-way valve 23 for allowing the refrigerant flow from the second valves 18a, 18b to the receiver 7 and preventing refrigerant flow from the receiver 7 to the second valves 18a, 18b so that the refrigerant from the second valves 18a, 18b flows into the pressurized liquid refrigerant path 17 through the receiver 7.