JP4161871B2 - Refrigeration cycle equipment - Google Patents

Description

  The present invention relates to a refrigeration cycle apparatus using a vortex tube, and more particularly to a refrigeration cycle apparatus used as a water heater.

  A generally well-known refrigeration cycle apparatus includes a refrigerant circuit by sequentially connecting a compressor, a radiator, a decompressor, and an evaporator. In this case, the amount of heat dissipated in the radiator is determined by the amount of heat absorbed in the evaporator and the input amount of the compressor. Therefore, in order to increase the efficiency of such a refrigeration cycle apparatus, there is no choice but to improve the performance of individual devices such as a compressor, a radiator, an evaporator and a blower, and there is a limit to the performance improvement.

  Then, the possibility of the performance improvement in a freezing apparatus is examined using a vortex tube. For example, the refrigerant at the outlet of the radiator is introduced into the refrigerant supply port of the vortex tube to generate a high-speed vortex, and the energy is separated into the high-temperature refrigerant and the low-temperature refrigerant and led out from the two outlets facing each other. A refrigeration cycle has been proposed in which evaporating ability is improved by supplying a low-temperature refrigerant to a decompressor so that the decompression process is close to isentropic expansion (see, for example, Patent Document 1).

  Further, hydrocarbons containing fluorine atoms (fluorocarbons) have been used as the refrigerant sealed in the refrigeration cycle apparatus. However, chlorofluorocarbons are not always satisfactory refrigerants because they have the property of destroying the ozone layer, and because they have a long life in the atmosphere and have a large greenhouse effect, they affect global warming. . Therefore, instead of chlorofluorocarbons, the possibility of a refrigeration cycle apparatus that uses carbon dioxide, ethane, etc. as a refrigerant, which has an ozone depletion potential of zero and a global warming potential that is much smaller than that of chlorofluorocarbons, has been studied. A refrigeration cycle apparatus that uses as a refrigerant has been proposed (see, for example, Patent Document 2).

Further, carbon dioxide has a critical temperature as low as 31.06 ° C., and does not condense on the high pressure side (compressor outlet to radiator to decompressor inlet) of a normal refrigeration cycle apparatus, and is operated at a critical pressure or higher. Since it becomes a critical cycle, a refrigeration cycle apparatus (for example, a hot water supply apparatus) that uses this characteristic and heats a fluid (for example, water) to a high temperature of about 60 ° C. or more with a radiator has been proposed.
JP-A-8-303879 (page 5, FIG. 1) Japanese Patent Publication No. 7-18602

  However, in the case of the prior art disclosed in Patent Document 1, the high-temperature refrigerant separated by the vortex tube is supplied again to the radiator. For this reason, when the temperature of this high-temperature refrigerant is lower than the temperature of the refrigerant discharged from the compressor, the temperature of the refrigerant at the radiator inlet portion decreases, and as a result, in the radiator, the heat exchange fluid and refrigerant The temperature difference between the refrigeration cycle apparatus and the heat dissipation amount is reduced, and the efficiency of the refrigeration cycle apparatus is reduced and the equipment is enlarged.

  In particular, in a refrigeration cycle apparatus (for example, a hot water supply apparatus) that uses carbon dioxide as a refrigerant that heats a fluid (for example, water) to a high temperature of about 60 ° C. or higher with a radiator, the discharge temperature of the compressor can be increased. Therefore, a decrease in the amount of heat released due to a decrease in the temperature of the refrigerant supplied to the radiator leads to a decrease in the temperature of the fluid used (for example, water), and the efficiency of the refrigeration cycle apparatus is reduced. There was a problem of increasing the size.

  Then, this invention constitutes the refrigerating cycle device which solved the above-mentioned subject, and it aims at achieving the improvement in efficiency of a refrigerating cycle device, and size reduction of an apparatus.

The refrigeration cycle apparatus of the present invention according to claim 1 comprises at least a compressor, a radiator, a vortex tube, and an evaporator to form a refrigerant circuit, and an inlet portion of the vortex tube is connected to a refrigerant flow of the radiator. A high temperature outlet portion of the vortex tube is connected to a second inlet portion located downstream of the inlet portion of the radiator in the refrigerant flow path of the radiator, and the low temperature outlet of the vortex tube Are connected to the refrigerant inlet portion of the evaporator, and the second inlet portion is provided in the vicinity of the point where the temperature difference between the refrigerant in the refrigerant flow path and the fluid that cools the refrigerant in the radiator is minimized. It is the refrigeration cycle apparatus characterized by being provided .

  The refrigeration cycle apparatus according to a second aspect of the present invention is the refrigeration cycle apparatus according to the present invention, characterized in that a bypass passage that bypasses the vortex tube and a decompressor are provided in the bypass passage.

  The refrigeration cycle apparatus of the present invention according to claim 3 is the refrigeration cycle apparatus of the present invention, wherein the low temperature outlet portion of the vortex tube is connected to the refrigerant inlet portion of the evaporator via a decompressor. .

According to a fourth aspect of the present invention, there is provided a refrigeration cycle apparatus according to the present invention, wherein at least a compressor, a radiator, a vortex tube, a gas-liquid separator, a decompressor and an evaporator are connected in a ring shape to constitute a refrigerant circuit, Is connected to the outlet portion of the refrigerant flow path of the radiator, the high temperature outlet portion of the vortex tube is connected to a second inlet portion located downstream of the inlet portion in the refrigerant flow path of the radiator, The low temperature outlet of the vortex tube is connected to the inlet of the gas-liquid separator, the gas outlet of the gas-liquid separator is connected to the suction part or the intermediate pressure part of the compressor, and the gas-liquid separator A liquid outlet portion is connected to the refrigerant inlet portion of the evaporator via the decompressor, and the refrigerant in the refrigerant flow path and the fluid that cools the refrigerant in the radiator
In the refrigeration cycle apparatus, the second inlet portion is provided in the vicinity of a portion where the temperature difference is minimized .

The refrigeration cycle apparatus of the present invention according to claim 5 is the refrigeration cycle apparatus of the present invention, wherein the vortex tube and the gas-liquid separator have an integral structure .

The refrigeration cycle apparatus of the present invention according to claim 6 comprises at least a compressor, a radiator, a vortex tube, a decompressor and an evaporator to form a refrigerant circuit, and an inlet portion of the vortex tube is connected to the radiator. Connected to an outlet portion of the first refrigerant flow path, a high temperature outlet portion of the vortex tube is connected to an inlet portion of a second refrigerant flow path of the radiator, and an outlet portion of the second refrigerant flow path is connected to the decompressor. To the refrigerant inlet portion of the evaporator, the low temperature outlet portion of the vortex tube is connected to the refrigerant inlet portion of the evaporator, and the refrigerant in the refrigerant and the radiator in the first refrigerant flow path. in the vicinity of the portion where the temperature difference between the fluid to be cooled is minimum, it is a refrigeration cycle apparatus according to claim inlet portion of the second fluid flow path is provided.

Refrigeration cycle apparatus of the present invention of claim 7, wherein the pressure of the high pressure side of the refrigerant circuit is a refrigeration cycle apparatus of the present invention, characterized in that operating at or above the critical pressure of the refrigerant.

The refrigeration cycle apparatus of the present invention according to claim 8 is the refrigeration cycle apparatus of the present invention, wherein the refrigerant sealed in the refrigerant circuit is carbon dioxide.

The refrigeration cycle apparatus of the present invention according to claim 9 is the refrigeration cycle apparatus of the present invention, wherein the fluid is heated to a high temperature of about 60 ° C. or more by the radiator.

According to the present invention, at least a compressor, a radiator, a vortex tube, and an evaporator are connected in an annular shape to form a refrigerant circuit, and the inlet portion of the vortex tube is connected to the outlet portion of the refrigerant flow path of the radiator. And connecting the high temperature outlet of the vortex tube to a second inlet located downstream of the inlet of the radiator in the refrigerant flow path of the radiator, and connecting the low temperature outlet of the vortex tube to the evaporator The second inlet portion is provided in the vicinity of the portion where the temperature difference between the refrigerant in the first refrigerant flow path and the fluid that cools the refrigerant in the radiator is minimized. Therefore, the amount of refrigerant sucked into the compressor is reduced by the amount re-supplied to the condenser, and the input amount of the compressor is reduced. Furthermore, the expansion ability close to the isentropic expansion in the vortex tube increases the evaporation capacity, and the evaporation pressure (that is, the suction pressure of the compressor) increases, so that the input amount of the compressor is reduced. Furthermore, since the high-temperature refrigerant led out from the vortex tube is re-supplied to the intermediate portion of the radiator, the refrigerant temperature in the section where the temperature difference between the refrigerant and the fluid is small can be raised. Therefore, the refrigeration cycle apparatus can be operated efficiently, and further, the apparatus can be downsized.

  Furthermore, according to the present invention, a bypass flow path that bypasses the vortex tube, and a pressure reducer provided in the bypass flow path, the refrigerant flow rate supplied to the vortex tube (or by adjusting the opening of the pressure reducer) (or The amount of refrigerant sucked into the compressor can be adjusted, and the refrigerant pressure and capacity can be easily adjusted.

  Furthermore, according to the present invention, the low temperature outlet portion of the vortex tube is connected to the refrigerant inlet portion of the evaporator via a decompressor, thereby increasing the refrigerant temperature in the section where the temperature difference between the refrigerant and the fluid is the smallest. Therefore, efficient operation of the refrigeration cycle apparatus is possible, and further downsizing of the apparatus is possible.

  Further, according to the present invention, since the low temperature outlet portion of the vortex tube is connected to the refrigerant inlet portion of the evaporator via the decompressor, the increase in evaporation capacity is reduced, but the opening of the decompressor By performing the adjustment, the refrigerant pressure and capacity can be easily adjusted.

Furthermore, according to the present invention, at least a compressor, a radiator, a vortex tube, a gas-liquid separator, a decompressor and an evaporator are connected to form a refrigerant circuit, and an inlet portion of the vortex tube is connected to the radiator. A high-temperature outlet portion of the vortex tube is connected to a second inlet portion located downstream of the inlet portion in the refrigerant flow passage of the radiator, and the low-temperature outlet portion of the vortex tube Is connected to the inlet portion of the gas-liquid separator, the gas outlet portion of the gas-liquid separator is connected to the suction portion or the intermediate pressure portion of the compressor, and the liquid outlet portion of the gas-liquid separator is connected to the decompressor in the vicinity of the portion where the temperature difference is the smallest of the respective refrigerant inlet portion of the evaporator is connected, the fluid for cooling the coolant in the radiator and the refrigerant of the first refrigerant flow path through the second By the mouth portion is provided, for the gas refrigerant separated by the gas-liquid separator is supplied to the compressor by bypassing the evaporator, the amount of coolant flowing through the evaporator is reduced, the evaporator Since the pressure loss can be reduced and the evaporation pressure (that is, the suction pressure of the compressor) increases, the input amount of the compressor is reduced. Furthermore, the refrigerant pressure and capacity can be easily adjusted by adjusting the opening of the decompressor.

  Furthermore, according to the present invention, the vortex tube and the gas-liquid separator have an integral structure, so that the device can be downsized.

Furthermore, according to the present invention, at least a compressor, a radiator, a vortex tube, a decompressor, and an evaporator are connected in a ring to form a refrigerant circuit, and an inlet portion of the vortex tube is connected to the first of the radiator. Connect to the outlet of the refrigerant flow path, connect the high temperature outlet of the vortex tube to the inlet of the second refrigerant flow path of the radiator, and connect the outlet of the second refrigerant flow path through the pressure reducer A fluid that is connected to a refrigerant inlet of the evaporator, connects a low temperature outlet of the vortex tube to a refrigerant inlet of the evaporator, and cools the refrigerant in the refrigerant in the first refrigerant channel and the radiator in the vicinity of the portion where the temperature difference is the smallest and, by the second inlet portion is provided, the high-temperature refrigerant derived from the vortex tube is re-supplied to the middle portion of the radiator Because, it is possible to increase the refrigerant temperature interval the temperature difference between the refrigerant and the fluid is small. Further, by adjusting the opening of the decompressor, the refrigerant pressure and capacity can be easily adjusted .

Further , according to the present invention, by operating the pressure on the high pressure side of the refrigerant circuit above the critical pressure of the refrigerant, a change in latent heat is performed in the radiator as compared with the case of operating at a pressure below the supercritical. Therefore, since the temperature change of the refrigerant in the radiator becomes gentle, it is necessary to supply the high-temperature refrigerant derived from the vortex tube so as to exchange heat with the refrigerant in the vicinity of the section where the temperature difference between the refrigerant and the fluid is the smallest. It is desirable to use the radiator efficiently, and it is possible to operate the refrigeration cycle apparatus more efficiently and downsize the equipment.

  Further, according to the present invention, since the refrigerant sealed in the refrigerant circuit is carbon dioxide, the discharge temperature is likely to be higher than the high-temperature refrigerant derived from the vortex tube, and therefore, the refrigerant circuit is derived from the vortex tube. The effect of supplying high-temperature refrigerant to heat exchange with refrigerant in the vicinity of the section where the temperature difference between the refrigerant and the fluid is the smallest is significant, enabling more efficient operation of the refrigeration cycle apparatus and miniaturization of equipment. Become.

Further, according to the present invention, since the fluid is heated to a high temperature of about 60 ° C. or higher by the radiator, the discharge temperature is likely to be higher than the high-temperature refrigerant derived from the vortex tube. It is desirable to supply the derived high-temperature refrigerant so as to exchange heat with the refrigerant in the vicinity of the section where the temperature difference between the refrigerant and the fluid is the smallest, which enables more efficient operation of the refrigeration cycle apparatus and miniaturization of equipment. Become.

In the first embodiment of the present invention, at least a compressor, a radiator, a vortex tube and an evaporator are annularly connected to form a refrigerant circuit, and an inlet portion of the vortex tube is connected to a refrigerant flow of the radiator. A high temperature outlet portion of the vortex tube is connected to a second inlet portion located downstream of the inlet portion of the radiator in the refrigerant flow path of the radiator, and the low temperature outlet of the vortex tube Are connected to the refrigerant inlet portion of the evaporator, and the second inlet portion is provided in the vicinity of the point where the temperature difference between the refrigerant in the refrigerant flow path and the fluid that cools the refrigerant in the radiator is minimized. It is what has been . According to the present embodiment, the amount of refrigerant sucked into the compressor is reduced by the amount re-supplied to the condenser, and the input amount of the compressor is reduced. Furthermore, the expansion ability close to the isentropic expansion in the vortex tube increases the evaporation capacity, and the evaporation pressure (that is, the suction pressure of the compressor) increases, so that the input amount of the compressor is reduced. Furthermore, since the high-temperature refrigerant led out from the vortex tube is re-supplied to the intermediate portion of the radiator, the refrigerant temperature in the section where the temperature difference between the refrigerant and the fluid is small can be raised. Therefore, the refrigeration cycle apparatus can be operated efficiently, and further, the apparatus can be downsized.

  The second embodiment according to the present invention further includes a bypass channel that bypasses the vortex tube, and a decompressor in the bypass channel. According to the present embodiment, the flow rate of the refrigerant supplied to the vortex tube (or the amount of refrigerant sucked into the compressor) can be adjusted by adjusting the opening of the decompressor, and the pressure of the refrigerant Adjustment and capacity adjustment can be performed easily.

  In the third embodiment according to the present invention, the low-temperature outlet of the vortex tube is further connected to the refrigerant inlet of the evaporator via a decompressor. According to the present embodiment, although the increase amount of the evaporation capacity is further reduced, the refrigerant pressure and capacity can be easily adjusted by adjusting the opening of the decompressor.

According to a fourth embodiment of the present invention, at least a compressor, a radiator, a vortex tube, a gas-liquid separator, a decompressor, and an evaporator are annularly connected to constitute a refrigerant circuit, and an inlet of the vortex tube The vortex tube is connected to an outlet of the refrigerant flow path of the radiator, and the high temperature outlet of the vortex tube is connected to a second inlet located downstream of the inlet in the refrigerant flow path of the radiator. A low-temperature outlet of the tube is connected to an inlet of the gas-liquid separator, a gas outlet of the gas-liquid separator is connected to a suction part or an intermediate pressure part of the compressor, and a liquid outlet of the gas-liquid separator the section through the pressure reducer is connected to the refrigerant inlet portion of the evaporator, in the vicinity of the portion where the temperature difference is the smallest of the fluid for cooling the refrigerant in the radiator and the refrigerant of the refrigerant flow path, before In which the second inlet portion is provided. According to the present embodiment, since the gas refrigerant separated by the gas-liquid separator bypasses the evaporator and is supplied to the compressor, the amount of refrigerant flowing through the evaporator decreases, Since the pressure loss can be reduced and the evaporation pressure (that is, the suction pressure of the compressor) increases, the input amount of the compressor is reduced. Furthermore, the refrigerant pressure and capacity can be easily adjusted by adjusting the opening of the decompressor.

  In the fifth embodiment according to the present invention, the vortex tube and the gas-liquid separator have an integral structure. According to the present embodiment, the device can be further downsized.

In the sixth embodiment of the present invention, at least a compressor, a radiator, a vortex tube, a decompressor and an evaporator are annularly connected to form a refrigerant circuit, and an inlet portion of the vortex tube is connected to the radiator. Connected to an outlet portion of the first refrigerant flow path, a high temperature outlet portion of the vortex tube is connected to an inlet portion of a second refrigerant flow path of the radiator, and an outlet portion of the second refrigerant flow path is connected to the decompressor. To the refrigerant inlet portion of the evaporator, the low temperature outlet portion of the vortex tube is connected to the refrigerant inlet portion of the evaporator, and the refrigerant in the refrigerant and the radiator in the first refrigerant flow path. in the vicinity of the portion where the temperature difference between the fluid to be cooled is minimum, in which the inlet portion of the second fluid flow path is provided. According to the present embodiment, since the high-temperature refrigerant derived from the vortex tube is re-supplied to the intermediate part of the radiator, the fluid temperature in the section where the temperature difference between the refrigerant and the fluid is small can be raised. Further, by adjusting the opening of the decompressor, the refrigerant pressure and capacity can be easily adjusted. Therefore, the refrigeration cycle apparatus can be operated efficiently, and further, the apparatus can be downsized.

  First, the refrigeration cycle apparatus of the present invention will be described.

  FIG. 1 is a schematic configuration diagram showing a hot water supply apparatus which is an embodiment of the refrigeration cycle apparatus of the present invention.

  As shown in FIG. 1, the refrigeration cycle apparatus according to the present embodiment includes a compressor 1, a first refrigerant flow path 2A of a radiator 2 as a heat exchanger for hot water supply, a vortex tube 3, and an evaporator using outside air as a heat source. 4 and the like, and a fluid circuit B including a water supply pump 6, a fluid flow path 2B of the radiator 2, a hot water supply tank 7, and the like. In the first refrigerant channel 2A, the inlet 3a of the vortex tube 3 is connected to the outlet 2b of the first refrigerant channel 2A of the radiator 2, and the high temperature outlet 3b of the vortex tube 3 is the second of the radiator 2. It is connected to a second inlet 2c located downstream from the inlet 2a of one refrigerant flow path 2A, and the low temperature outlet 3c of the vortex tube 3 is connected to the refrigerant inlet of the evaporator 4, respectively. Further, a check valve 5 is provided in a pipe connecting the high temperature outlet 3b of the vortex tube 3 and the second inlet 2c of the first refrigerant flow path 2A.

  The vortex tube 3 is designed so that the amount of the low-temperature refrigerant derived from the low-temperature outlet portion 3c is considerably larger than that of the high-temperature refrigerant derived from the high-temperature outlet portion 3b.

  Next, the operation of the refrigeration cycle apparatus configured as described above will be described. In the refrigerant circuit A, carbon dioxide, which is a refrigerant, is compressed by the compressor 1 to a pressure exceeding the critical pressure. The compressed refrigerant becomes a high-temperature and high-pressure state, and dissipates heat to the fluid (for example, water) flowing through the fluid passage 2B when flowing from the inlet portion 2a of the first refrigerant passage 2A of the radiator 2 to the outlet portion 2b. Then cooled. Thereafter, the refrigerant is supplied to the inlet 3 a of the vortex tube 3. The high-pressure refrigerant supplied to the vortex tube 3 is separated into a high-temperature refrigerant and a low-temperature refrigerant by energy separation in the vortex tube 3. The high-temperature refrigerant is re-supplied from the high-temperature outlet 3 b of the vortex tube 3 to the second inlet 2 c of the first refrigerant flow path 2 A of the radiator 2. On the other hand, the low-temperature and low-pressure gas-liquid two-phase low-temperature refrigerant is supplied to the evaporator 4 from the low-temperature outlet 3c. That is, the vortex tube 3 also functions as a decompressor. In the evaporator 4, the refrigerant is heated by air or the like, becomes a gas-liquid two-phase or gas state, and is sucked into the compressor 1 again.

  In the fluid circuit B, the fluid (for example, water) sent from the bottom of the hot water supply tank 7 to the fluid flow path 2B of the radiator 2 by the water supply pump 6 is heated by the refrigerant flowing through the first refrigerant flow path 2A, It becomes a fluid (for example, hot water), and the high temperature fluid is stored from the top of the hot water supply tank 36. By repeating such a cycle, the refrigeration cycle apparatus of the present embodiment can be used as a water heater.

In the refrigeration cycle apparatus configured as described above, the following effects can be obtained. First, the amount of refrigerant sucked into the compressor 1 is reduced by the amount re-supplied to the condenser 2, and the input amount of the compressor 1 is reduced. Next, in the vortex tube 3, expansion close to isentropic expansion is obtained. That is, as shown in FIG. 2, in a refrigeration cycle apparatus using a conventional pressure reducer, a cycle indicated by a broken line a → b → c → d → a is obtained, and an isoenthalpy expansion is obtained in c → d. On the other hand, in the present embodiment using the vortex tube 3, a cycle indicated by a → b → c → e → a indicated by a solid line is obtained, and substantially isentropic expansion is obtained in c → e. Accordingly, in the evaporator 4, the enthalpy between ed increases, so that the evaporation capacity increases, and the evaporation pressure (that is, the suction pressure of the compressor 1) rises. The amount is reduced. Furthermore, since the high-temperature refrigerant led out from the vortex tube 3 is re-supplied to the second inlet 2c, which is an intermediate part of the refrigerant flow path 2A of the radiator 2, the amount of heat released from the radiator 2 can be increased. That is, as shown in FIG. 3, in the conventional refrigeration cycle apparatus, the temperature change of the refrigerant and the fluid in the radiator 2 becomes a temperature change as indicated by a broken line, whereas the intermediate portion of the refrigerant flow path 2A. In the present embodiment in which the high-temperature refrigerant is re-supplied, the temperature changes as shown by the solid line. That is, conventionally, since the high-temperature refrigerant is supplied again in the vicinity of the section X in FIG. 3 where the temperature difference between the refrigerant and the fluid is the smallest, the refrigerant temperature in this section can be raised. Therefore, even when the temperature difference between the refrigerant and the fluid is the same as that of the conventional one, it is possible to take out a fluid having a higher temperature. Due to these effects, efficient operation of the refrigeration cycle apparatus can be achieved in this embodiment, and further, the apparatus can be downsized.

  Next, a refrigeration cycle apparatus according to another embodiment will be described with reference to FIG. FIG. 4 is a schematic configuration diagram showing a refrigerant circuit of the refrigeration cycle apparatus of the present invention. 4, the same components as those in FIG. 1 are given the same reference numerals as those in FIG.

  In the refrigeration cycle apparatus of FIG. 4, piping 11 is provided between the outlet 2 b of the radiator 2 and the inlet 3 a of the vortex tube 3, and between the low temperature outlet 3 c of the vortex tube 3 and the refrigerant inlet of the evaporator 4. (That is, a flow path that bypasses the vortex tube 3 is formed), and a decompressor 12 is provided.

  In the refrigeration cycle apparatus configured as described above, the following effects can be obtained in addition to the effects of the previous embodiment. By adjusting the opening of the decompressor 12, the flow rate of refrigerant supplied to the vortex tube 3 (or the amount of refrigerant sucked into the compressor 1) can be adjusted, and refrigerant pressure adjustment and capacity adjustment are easy. Yes.

  Therefore, in the present embodiment, more efficient operation of the refrigeration cycle apparatus and downsizing of the device are possible.

  Furthermore, a refrigeration cycle apparatus according to another embodiment will be described with reference to FIG. FIG. 5 is a schematic configuration diagram showing a refrigerant circuit of the refrigeration cycle apparatus of the present invention. In FIG. 5, the same components as those in FIG. 1 are given the same reference numerals as those in FIG.

  In the refrigeration cycle apparatus of FIG. 5, a decompressor 21 is installed between the low temperature outlet 3 c of the vortex tube 3 and the refrigerant inlet of the evaporator 4.

  In the refrigeration cycle apparatus configured as described above, the following effects can be obtained in addition to the effects of the previous embodiment. As shown in FIG. 6, the expansion close to the isentropic expansion in the vortex tube 3 is only between c → f, and between f → g is the isoenthalpy expansion in the decompressor 21, so in the evaporator 4, Although only the enthalpy between g and d is increased and the increase in the evaporation capacity is reduced, the pressure adjustment and capacity adjustment of the refrigerant can be easily performed by adjusting the opening of the decompressor 21.

  Therefore, in the present embodiment, more efficient operation of the refrigeration cycle apparatus and downsizing of the device are possible.

  Furthermore, a refrigeration cycle apparatus according to another embodiment will be described with reference to FIG. FIG. 7 is a schematic configuration diagram showing a refrigerant circuit of the refrigeration cycle apparatus of the present invention. In FIG. 7, the same components as those in FIG. 1 are given the same numbers as in FIG.

  In the refrigeration cycle apparatus of FIG. 7, the low-temperature outlet 3 c of the vortex tube 3 is connected to the inlet 31 a of the gas-liquid separator 31, and the gas outlet 31 b of the gas-liquid separator 31 is connected to the compressor 1 by a pipe 32. The liquid outlet 31 c of the gas-liquid separator 31 is connected to the refrigerant inlet of the evaporator 4 via the decompressor 33.

  Next, the operation of the refrigeration cycle apparatus configured as described above will be described. The high-temperature refrigerant separated by the vortex tube 3 is re-supplied from the high-temperature outlet portion 3b of the vortex tube 3 to the second inlet portion 2c of the first refrigerant channel 2A of the radiator 2. On the other hand, the low-temperature refrigerant in the gas-liquid two-phase state separated by the vortex tube 3 is depressurized to an intermediate pressure and is supplied from the low-temperature outlet part 3 c to the inlet part 31 a of the gas-liquid separator 31. In the gas-liquid separator 31, the liquid refrigerant and the gas refrigerant are separated using the difference in density between the refrigerant liquid and the gas. The gas refrigerant bypasses the evaporator 4 through the pipe 32 from the gas outlet portion 31 b and is supplied to the suction portion of the compressor 1. On the other hand, the liquid refrigerant is supplied from the liquid outlet 31 c to the decompressor 33, further decompressed by the decompressor 33, and then supplied to the evaporator 4. In the evaporator 4, the refrigerant is heated by air or the like, becomes a gas-liquid two-phase or gas state, and is sucked into the compressor 1 again.

  In the refrigeration cycle apparatus configured as described above, the following effects can be obtained in addition to the effects of the previous embodiment. First, as shown in FIG. 8, the expansion close to the isentropic expansion in the vortex tube 3 is only between c → f. However, in order to supply the liquid refrigerant separated by the gas-liquid separator 31 to the decompressor 33, the refrigerant supplied to the decompressor 33 is in the state of the h point, and the decompressor 33 has an equal enthalpy indicated by h → i. In the evaporator 4, since the enthalpy between i → d is increased in the evaporator 4 with respect to the refrigeration cycle apparatus using the conventional decompressor, the evaporation capacity is increased, and the evaporation pressure (that is, the compressor) 1), the input amount of the compressor 1 is reduced. Next, since the gas refrigerant separated by the gas-liquid separator 31 bypasses the evaporator 4 and is supplied to the compressor 1, the amount of refrigerant flowing through the evaporator 4 is reduced, and the pressure loss in the evaporator 4 is reduced. Since the evaporation pressure (that is, the suction pressure of the compressor 1) increases, the input amount of the compressor 1 is reduced. Furthermore, by adjusting the opening degree of the decompressor 33, the refrigerant pressure and capacity can be easily adjusted.

  Therefore, in the present embodiment, more efficient operation of the refrigeration cycle apparatus and downsizing of the device are possible.

  In the present embodiment, the gas-side outlet 31b of the gas-liquid separator 31 has been described as being connected to the suction side of the compressor 1, but may be connected to the intermediate pressure portion of the compressor 1, in this case Further, the amount of input in the compressor 1 can be reduced, and the refrigeration cycle apparatus can be operated efficiently.

Furthermore, a refrigeration cycle apparatus according to another embodiment will be described. In this embodiment, the vortex tube 3 and the gas-liquid separator 31 are integrally formed in the embodiment of FIG. FIG. 9 is a cross-sectional configuration diagram in which a vortex tube and a gas-liquid separator are integrally configured. In FIG. 9, reference numeral 41 denotes a cylindrical outer shell made of copper, aluminum, brass, or the like. Inside the outer shell 41, a threshold plate 41 a and a valve 41 b are provided. Here, the upper part of the threshold plate 41a acts as a vortex tube. When a high-pressure refrigerant is supplied in the cylindrical tangential direction of the outer shell 41 from an inlet portion 3a provided at a portion slightly above the threshold plate 41a, the refrigerant swirls around the inner wall of the outer shell 41 while forming a vortex. The flow toward the valve 41b is formed, and the high temperature refrigerant and the low temperature refrigerant are separated. That is, the high-temperature refrigerant is discharged from the high-temperature outlet portion 3b provided behind the valve, and the low-temperature refrigerant flows in the reverse direction through the central portion of the flow swirling around the peripheral wall inside the outer shell 41 and returns in the direction of the threshold plate 41a. .

  The threshold plate 41a is provided with a refrigerant passage which is a low temperature outlet portion 3c of the vortex tube and is also an inlet portion 31a of the gas-liquid separator, and the lower portion of the threshold plate 41a functions as a gas-liquid separator. That is, the low-temperature refrigerant separated by the vortex tube is supplied from the inlet 31a (and the low-temperature outlet 3c), and the liquid refrigerant accumulates at the bottom of the outer shell 41 due to the difference in density between the refrigerant liquid and the gas. The liquid refrigerant is discharged from the liquid outlet portion 31c provided at the bottom of the outer shell 41, and the liquid refrigerant is discharged from the gas outlet portion 3b provided slightly below the threshold plate 41a. And gas refrigerant.

  Since the operation of the refrigeration cycle is the same as in the previous embodiment, the description thereof will be omitted. In the refrigeration cycle apparatus configured as described above, in addition to the effects of the previous embodiment, the vortex tube and gas-liquid separation are performed. Since the device is integrated, the size of the device can be further reduced.

  Furthermore, a refrigeration cycle apparatus according to another embodiment will be described with reference to FIG. FIG. 10 is a schematic configuration diagram showing a refrigerant circuit of the refrigeration cycle apparatus of the present invention. In FIG. 10, the same components as those in FIG. 1 are given the same numbers as in FIG.

  In the refrigeration cycle apparatus of FIG. 10, in the radiator 2, the second refrigerant that exchanges heat with the fluid passage 2 </ b> B, separately from the first refrigerant passage 2 </ b> A that exchanges heat with the fluid passage 2 </ b> B through which a fluid (for example, water) flows. A flow path 2C is provided. The high temperature outlet 3b of the vortex tube 3 is connected to the inlet 2d of the second refrigerant channel 2C, and the outlet 2e of the second refrigerant channel 2C is connected to the refrigerant inlet of the evaporator 4 via the decompressor 33. Each is connected.

  The inlet 2d to the outlet 2e of the second refrigerant channel 2C are connected to the fluid channel 2B and the heat in the section where the temperature difference between the refrigerant in the first refrigerant channel 2A and the fluid flowing through the fluid channel 2B is the smallest. It is provided to replace.

  Next, the operation of the refrigeration cycle apparatus configured as described above will be described. The high-temperature refrigerant separated by the vortex tube 3 is supplied from the high-temperature outlet 3b of the vortex tube 3 to the inlet 2d of the second refrigerant channel 2C of the radiator 2, and the refrigerant in the first refrigerant channel 2A of the radiator 2 is supplied. After the heat exchange with the fluid flowing through the fluid flow path 2B in the section where the temperature difference between the fluid flowing through the fluid flow path 2B is the smallest, after flowing out from the outlet 2e of the second refrigerant flow path 2C, the decompressor 51 The refrigerant is decompressed, becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant, and is supplied to the evaporator 4. On the other hand, a low-temperature low-pressure gas-liquid two-phase low-temperature refrigerant flowing out from the low-temperature outlet 3 c of the vortex tube 3 is also supplied to the evaporator 4. In the evaporator 4, the refrigerant is heated by air or the like, becomes a gas-liquid two-phase or gas state, and is sucked into the compressor 1 again.

In the refrigeration cycle apparatus configured as described above, the following effects can be obtained. The high-temperature refrigerant derived from the vortex tube 3 is supplied to the second refrigerant flow path 2C provided in the vicinity of the section where the temperature difference between the refrigerant and the fluid in the first refrigerant flow path 2A of the radiator 2 is the smallest, and this section The amount of heat released can be increased by dissipating heat to the fluid from the second refrigerant flow path 2C. Therefore, even with the same temperature difference between the refrigerant and the fluid as in the prior art, a fluid having a higher temperature can be taken out. Further, by adjusting the opening of the decompressor 51, the flow rate of the refrigerant supplied to the vortex tube 3 can be adjusted, and the pressure adjustment and capacity adjustment of the refrigerant can be easily performed.

  Therefore, in the present embodiment, more efficient operation of the refrigeration cycle apparatus and downsizing of the device are possible.

  In this embodiment, as in the previous embodiment, another decompressor is provided on the downstream side of the low temperature outlet portion 3c of the vortex tube 3, or a flow path for bypassing the vortex tube 3 is provided. In addition, a flow rate of the refrigerant supplied to the vortex tube 3 may be adjusted by providing another pressure reducer and adjusting the opening of the pressure reducer.

  In the above embodiment, the high-temperature refrigerant derived from the vortex tube 3 is supplied in the first refrigerant flow path 2A of the radiator 2 so as to exchange heat with the refrigerant in the vicinity of the section where the temperature difference between the refrigerant and the fluid is the smallest. This is most desirable in efficiently using the radiator 2, and enables more efficient operation of the refrigeration cycle apparatus and downsizing of the equipment. Further, when the pressure on the high-pressure side of the refrigeration circuit is operated at a pressure higher than the supercritical pressure, since the latent heat is not changed in the radiator 2 as compared with the case of operating at a pressure lower than the supercritical temperature, Since the temperature change of the refrigerant in the vessel 2 becomes gentle, there is an effect by supplying the high-temperature refrigerant derived from the vortex tube 3 so as to exchange heat with the refrigerant in the vicinity of the section where the temperature difference between the refrigerant and the fluid is the smallest. Larger, more efficient operation of the refrigeration cycle apparatus and downsizing of the equipment are possible. Further, when the refrigerant is carbon dioxide, the discharge temperature is likely to be higher than that of the high-temperature refrigerant derived from the vortex tube 3, so the high-temperature refrigerant derived from the vortex tube 3 is used as the temperature of the refrigerant and the fluid. It is desirable to supply the refrigerant so that it exchanges heat with the refrigerant in the vicinity of the section where the difference is the smallest, so that the refrigeration cycle apparatus can be operated more efficiently and the equipment can be downsized. Further, when the fluid is heated to a high temperature of about 60 ° C. or more by the radiator 2, the discharge temperature is likely to be higher than the high-temperature refrigerant derived from the vortex tube 3, and thus the fluid is derived from the vortex tube 3. It is desirable to supply the high-temperature refrigerant so as to exchange heat with the refrigerant in the vicinity of the section where the temperature difference between the refrigerant and the fluid is the smallest, which enables more efficient operation of the refrigeration cycle apparatus and miniaturization of the equipment.

The block diagram which shows the refrigerating-cycle apparatus by one Example of this invention. Pressure and enthalpy diagram showing the operating point of the refrigeration cycle apparatus according to the same embodiment Temperature change diagram of refrigerant and water in the radiator according to the same example The block diagram which shows the refrigerating-cycle apparatus by another Example. The block diagram which shows the refrigerating-cycle apparatus by another Example. Pressure and enthalpy diagram showing the operating point of the refrigeration cycle apparatus according to the same embodiment The block diagram which shows the refrigerating-cycle apparatus by another Example. Pressure and enthalpy diagram showing the operating point of the refrigeration cycle apparatus according to the same embodiment Cross-sectional view of vortex tube / gas-liquid separator according to another embodiment The block diagram which shows the refrigerating-cycle apparatus by another Example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Compressor 2 Radiator 3 Vortex tube 4 Evaporator 5 Check valve 6 Water supply pump 7 Hot water supply tank 11, 32 Bypass flow path 12, 21, 33, 51 Pressure reducer 31 Gas-liquid separator 41 Outer shell

Claims (9)

At least a compressor, a radiator, a vortex tube and an evaporator are connected in an annular shape to form a refrigerant circuit, and an inlet portion of the vortex tube is connected to an outlet portion of a refrigerant flow path of the radiator, and the vortex tube Are connected to a second inlet located downstream from the inlet of the radiator in the refrigerant flow path of the radiator, and the cold outlet of the vortex tube is connected to the refrigerant inlet of the evaporator, respectively. The refrigeration cycle apparatus is characterized in that the second inlet portion is provided in the vicinity of a portion where the temperature difference between the refrigerant in the refrigerant flow path and the fluid that cools the refrigerant in the radiator is minimized. . The refrigeration cycle apparatus according to claim 1, further comprising: a bypass passage that bypasses the vortex tube; and a decompressor in the bypass passage. The refrigeration cycle apparatus according to claim 1, wherein a low temperature outlet portion of the vortex tube is connected to a refrigerant inlet portion of the evaporator via a decompressor. At least a compressor, a radiator, a vortex tube, a gas-liquid separator, a decompressor, and an evaporator are connected in a ring to form a refrigerant circuit, and the inlet of the vortex tube is connected to the outlet of the refrigerant flow path of the radiator A high temperature outlet portion of the vortex tube is connected to a second inlet portion located downstream of the inlet portion in the refrigerant flow path of the radiator, and the low temperature outlet portion of the vortex tube is connected to the gas-liquid separator. The gas outlet portion of the gas-liquid separator is connected to the suction portion or the intermediate pressure portion of the compressor, and the liquid outlet portion of the gas-liquid separator is connected to the evaporator via the decompressor. respectively to the refrigerant inlet portion of the connection, in the vicinity of the portion where the temperature difference is the smallest of the fluid for cooling the refrigerant in the radiator and the refrigerant of the refrigerant passage, said second inlet is provided Refrigeration cycle apparatus according to claim. The refrigeration cycle apparatus according to claim 4, wherein the vortex tube and the gas-liquid separator have an integral structure. At least a compressor, a radiator, a vortex tube, a decompressor and an evaporator are connected to form a refrigerant circuit, and an inlet portion of the vortex tube is connected to an outlet portion of the first refrigerant channel of the radiator, The high temperature outlet of the vortex tube is connected to the inlet of the second refrigerant channel of the radiator, and the outlet of the second refrigerant channel is connected to the refrigerant inlet of the evaporator via the decompressor. The low temperature outlet of the vortex tube is connected to the refrigerant inlet of the evaporator, and the temperature difference between the refrigerant in the first refrigerant channel and the fluid that cools the refrigerant in the radiator is minimized. A refrigerating cycle apparatus , wherein an inlet portion of the second fluid flow path is provided in the vicinity . Refrigeration cycle apparatus according to any one of claims 1 to 6 the pressure of the high pressure side, characterized in that it is operated at or above the critical pressure of the refrigerant of the refrigerant circuit. Refrigeration cycle apparatus according to any one of claims 1 to 7, characterized in that the refrigerant sealed in the refrigerant circuit is carbon dioxide. Refrigeration cycle apparatus according to any one of claims 1 to 8, characterized in that to heat the fluid to a temperature above about 60 ° C. at the radiator.

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