Refrigeration apparatus and heat exchanger used for refrigeration apparatus

Abstract

To provide a refrigeration apparatus and a heat exchanger used for the refrigeration apparatus capable of exhibiting the cooling capacity of the same level even if an alternate refrigerant is used without largely changing constituent parts of a refrigeration cycle. In the refrigeration apparatus according to the present invention, a ratio of the number of tubes of the supercooling section ( 17 ) to the total number of tubes ( 20 ) of the condensing section ( 16 ) and the supercooling section ( 17 ) is set such that cooling capacity obtained by an increased enthalpy difference with the same flow rate of refrigerant by the supercooling section ( 17 ) becomes equal to cooling capacity of a refrigeration cycle of the HFC134a refrigerant.

1 - 6 . (canceled) 
     
     
         7 . A refrigeration apparatus comprising:
 a compressor which uses an alternate refrigerant instead of an HFC134a refrigerant and compresses the alternate refrigerant;   a heat exchanger including a condensing section which condenses the compressed alternate refrigerant and a supercooling section which supercools the alternate refrigerant which passed through the condensing section;   a decompressing device which decompresses and expands the condensed alternate refrigerant;   an evaporator which evaporates the decompressed and expanded alternate refrigerant; and   a liquid receiving device which is disposed between the condensing section and the supercooling section, which gas-liquid separates the alternate refrigerant which passed through the condensing section, which stores the alternate refrigerant, and which supplies the alternate refrigerant to the supercooling section, wherein   the condensing section and the supercooling section have flow path cross sectional areas which become internal resistances, the condensing section and the supercooling section include a plurality of tubes arranged side by side through which the alternate refrigerant flows, a ratio of the number of tubes of the supercooling section to the total number of tubes of the condensing section and the supercooling section is set such that cooling capacity obtained by an increased enthalpy difference with the same flow rate of refrigerant by the supercooling section becomes equal to cooling capacity of a refrigeration cycle of the HFC134a refrigerant.   
     
     
         8 . The refrigeration apparatus according to claim  1 , wherein the ratio of the number of tubes of the supercooling section is 15 to 35% of the total number of tubes. 
     
     
         9 . The refrigeration apparatus according to claim  1 , wherein a radiation area ratio of the supercooling section is in a range of 20 to 35% of the entire area. 
     
     
         10 . The refrigeration apparatus according to claim  2 , wherein a radiation area ratio of the supercooling section is in a range of 20 to 35% of the entire area. 
     
     
         11 . The refrigeration apparatus according to claim  1 , wherein latent heat of vaporization of the alternate refrigerant is higher than that of the HFC134a refrigerant by 20% or higher, refrigerant liquid density of the alternate refrigerant is greater than that of the HFC134a refrigerant, and high pressure side (1500 kPa or higher) pressure of the compressor of the alternate refrigerant is lower than that of the HFC134a refrigerant if saturated temperature is the same. 
     
     
         12 . The refrigeration apparatus according to claim  2 , wherein latent heat of vaporization of the alternate refrigerant is higher than that of the HFC134a refrigerant by 20% or higher, refrigerant liquid density of the alternate refrigerant is greater than that of the HFC134a refrigerant, and high pressure side (1500 kPa or higher) pressure of the compressor of the alternate refrigerant is lower than that of the HFC134a refrigerant if saturated temperature is the same. 
     
     
         13 . The refrigeration apparatus according to claim  3 , wherein latent heat of vaporization of the alternate refrigerant is higher than that of the HFC134a refrigerant by 20% or higher, refrigerant liquid density of the alternate refrigerant is greater than that of the HFC134a refrigerant, and high pressure side (1500 kPa or higher) pressure of the compressor of the alternate refrigerant is lower than that of the HFC134a refrigerant if saturated temperature is the same. 
     
     
         14 . The heat exchanger used for the refrigeration apparatus according to claim  1 , wherein
 the condensing section and the supercooling section have flow path cross sectional areas which become internal resistances, the condensing section and the supercooling section include a plurality of tubes arranged side by side through which the alternate refrigerant flows, radiation fins are provided between the tubes, a ratio of the condensing section and the supercooling section can be changed by a connection position of the liquid receiving device and with this, the heat exchanger is commonly used as a heat exchanger using HFC134a refrigerant.   
     
     
         15 . A refrigeration apparatus comprising:
 a compressor which uses an alternate refrigerant instead of an HFC134a refrigerant and compresses the alternate refrigerant;   a heat exchanger including a condensing section which condenses the compressed alternate refrigerant and a supercooling section which supercools the alternate refrigerant which passed through the condensing section;   a decompressing device which decompresses and expands the condensed alternate refrigerant;   an evaporator which evaporates the decompressed and expanded alternate refrigerant; and   a liquid receiving device which is disposed between the condensing section and the supercooling section, which gas-liquid separates the alternate refrigerant which passed through the condensing section, which stores the alternate refrigerant, and which supplies the alternate refrigerant to the supercooling section, wherein   the condensing section and the supercooling section have flow path cross sectional areas which become internal resistances, the condensing section and the supercooling section include a plurality of tubes arranged side by side through which the alternate refrigerant flows, a ratio of the number of tubes of the supercooling section to the total number of tubes of the condensing section and the supercooling section is in a range of 15 to 35% of the total number of tubes.