JP2006266655A - Refrigerating device, refrigerator, and gas-liquid separator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerating device capable of restraining a desiccant from being crushed even in the case of using a refrigerant such as carbon dioxide, and to provide a refrigerator, and a gas-liquid separator provided in a refrigerating cycle. <P>SOLUTION: The refrigerating device 30 comprises a compressor 1; a radiator 2 connected to the discharge side of the compressor 1; a pressure reducing means connected to the outlet side of the radiator 2; and a heat sink 14 connected to the outlet side of the pressure reducing means. The refrigerating device 30 is constituted such that the refrigerant flowing out of the heat sink 14 is led into a suction port of the compressor 1. The pressure reducing means comprises a first pressure reducing means 31 and a second pressure reducing means 12 or 13, and the gas-liquid separator 4 is provided between the first pressure reducing means 31 and the second pressure reducing means 12 or 13. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a refrigeration apparatus having a moisture adsorbing means in a refrigerant, a refrigerator, and a gas-liquid separator that is provided in these refrigeration cycles and performs gas-liquid separation of a gas-liquid mixed refrigerant.

  In general, in a refrigeration apparatus having a refrigeration cycle equipped with a compressor or the like, the inside of a pipe may be frozen by moisture mixed in the refrigeration cycle, which may reduce the reliability of the refrigeration cycle. In such a refrigeration apparatus, as a means for preventing freezing as described above, it is known to arrange a dryer as a moisture removing means in the refrigeration cycle.

In Patent Document 1, in a refrigeration apparatus including a compressor, a condenser, an expansion valve, an evaporator, and the like, the refrigerant is mixed in the refrigerant between the condenser outlet side and the expansion valve inlet side, which are the high pressure side of the refrigeration cycle. It is described that a dryer filled with zeolite or the like for removing moisture is arranged.
Japanese Patent Laid-Open No. 11-21548

  By the way, in this type of refrigeration apparatus, for example, carbon dioxide or the like whose high pressure side may be operated at a supercritical pressure may be used as a refrigerant. In such a refrigeration apparatus using a carbon dioxide refrigerant, the high pressure side of the refrigeration cycle is higher in temperature and pressure than refrigerants such as HFC (hydrofluorocarbon), and thus a dryer is provided on the high pressure side of the refrigeration cycle as in the conventional case. When provided, the desiccant filled inside the dryer may be crushed.

  Therefore, an object of the present invention is to provide a refrigeration apparatus, a refrigerator, and a gas-liquid separator provided in these refrigeration cycles that can suppress crushing of the desiccant even when a refrigerant such as carbon dioxide is used. To do.

  The refrigeration apparatus of the present invention includes a compressor, a radiator connected to the discharge side of the compressor, a first decompression unit connected to the outlet side of the radiator, and a series of the first decompression unit. In a refrigeration apparatus comprising a refrigeration cycle including a second decompression unit connected to the heat sink, and a heat absorber connected to an outlet side of the second decompression unit, the outlet side of the first decompression unit and the Adsorption means for adsorbing moisture in the refrigerant is provided between the inlet side of the second decompression means.

  The gas-liquid separator of the present invention includes a container in which a mixed refrigerant of gas and liquid is introduced and gas and liquid are separated inside, an introduction pipe for introducing the refrigerant into the container, A first outlet pipe from which the separated gas refrigerant flows out; and a second outlet pipe from which the liquid refrigerant separated in the container flows out, and adsorbs moisture in the refrigerant in the container. It is characterized by having an adsorption part for the purpose.

  The refrigeration apparatus according to claim 3 includes a compressor, a radiator connected to a discharge side of the compressor, a first decompression unit connected to an outlet side of the radiator, and the first decompression. In the refrigeration apparatus comprising a refrigeration cycle including a second decompression means connected in series with the means and a heat absorber connected to the outlet side of the second decompression means, the outlet of the first decompression means The gas-liquid separator according to claim 2 is provided between the side and the inlet side of the second decompression means.

  According to a fourth aspect of the present invention, in the refrigeration apparatus according to the third aspect, the compressor has an intermediate pressure portion, and the first outlet pipe of the gas-liquid separator is connected to the intermediate pressure portion. It is characterized by.

  The invention according to claim 5 is the refrigeration apparatus according to any one of claims 1, 3, or 4, wherein the high-pressure portion of the refrigeration cycle is operated at a supercritical pressure. To do.

  A sixth aspect of the present invention is characterized in that in the refrigeration apparatus according to any one of the first, third, fourth, or fifth aspect, carbon dioxide is used as a refrigerant.

  A refrigerator according to the present invention includes the refrigeration apparatus according to any one of claims 1, 3, 4, 5, and 6.

  ADVANTAGE OF THE INVENTION According to this invention, even when refrigerant | coolants, such as a carbon dioxide, are used, the freezing apparatus and refrigerator which can suppress crushing of a desiccant are provided. Furthermore, according to the present invention, there are provided a refrigeration apparatus, a refrigerator, and a gas-liquid separator provided in these refrigeration cycles, which can improve performance even when the gas phase component of the refrigerant that does not contribute to heat exchange in the heat absorber is large.

  The present invention provides a refrigeration apparatus, a refrigerator, and a gas-liquid separator provided in these refrigeration cycles that can suppress crushing of the desiccant even when a refrigerant such as carbon dioxide is used. Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  An embodiment of the present invention will be described in detail with reference to the drawings. FIG. 1 shows a refrigerant circuit diagram of a refrigerating apparatus as one embodiment of the present invention.

  The refrigeration apparatus 30 includes a compressor 1, a radiator 2 connected to the discharge side of the compressor 1, a third capillary tube 31 connected to the outlet side of the radiator 2, and the third capillary tube 31. The gas-liquid separator 4 connected to the outlet side of the gas, the heat absorption means 8 through which the liquid refrigerant separated by the gas-liquid separator flows, the refrigerant discharged from the heat absorption means 8 and the refrigerant in the vicinity of the third capillary tube 31 And a first heat exchanger 15 configured to be capable of exchanging heat, and a refrigerant introduction pipe 6 through which a gas refrigerant separated by the gas-liquid separator 4 flows is provided in the intermediate pressure portion of the compressor 1 as a first heat. The outlet side of the exchanger 15 is connected to the suction port of the compressor 1 to constitute a refrigeration cycle.

  The refrigerant introduction pipe 6 between the gas-liquid separator 4 and the intermediate pressure portion of the compressor 1 is provided with a check valve 7 and between the first heat exchanger 15 and the suction port of the compressor 1. Is provided with a check valve 53.

  The heat absorbing means 8 includes a three-way valve 91, a first capillary tube 12, a second capillary tube 13 provided in parallel with the first capillary tube 12 and having a higher resistance value than the first capillary tube 12, and the first capillary tube 12. And a heat absorber 14 connected after the junction 9A where the refrigerant pipes from the second capillary tubes 12 and 13 merge. The heat absorbing means 8 functions selectively in different temperature zones, and when the liquid refrigerant discharged from the gas-liquid separator 4 flows to the first capillary tube 12 side by switching the three-way valve 91, the heat absorber 14 Refrigeration operation is performed by increasing the flow rate of the refrigerant flowing through.

  On the other hand, when the refrigerant flows to the second capillary tube 13 side by switching the three-way valve 91, the flow rate of the refrigerant flowing through the heat absorber 14 is reduced and the refrigeration operation is performed.

  In addition to the method of switching the first and second capillary tubes 12 and 13 as described above, the switching between the refrigeration operation and the freezing operation is performed by changing the rotational speed of the compressor 1 to change the heat absorber 14. It is also possible by controlling the flow rate of the refrigerant flowing through, and may be realized by combining these methods.

  The refrigeration apparatus 30 also includes selection means 23 that sends cool air generated in the heat absorber 14 by a fan (not shown) and selectively guides it to a plurality of chambers (the refrigerator compartment 21 and the freezer compartment 22) controlled in different temperature zones. Configured.

  The selection means 23 includes a blower duct 24 and a switching damper 25, and a duct 57 </ b> A is provided between the switching damper 25 and the refrigerator compartment 21, and a duct 58 </ b> A is provided between the freezer compartment 22. A control device 26 is connected to the switching damper 25. The control device 26 is connected to the above-described three-way valve 91. For example, during the refrigeration operation, the three-way valve 91 is switched to the second capillary tube 13 side, and the switching damper 25 is switched so that cold air flows through the duct 58A. Cold air is introduced into the freezer compartment 22 and the three-way valve 91 is switched to the first capillary tube 12 side during refrigeration operation, and the switching damper 25 is switched so that the cold air flows through the duct 57A to introduce cold air into the refrigerator compartment 21.

  The compressor 1 is a two-stage compressor, includes a first-stage compression unit 1A and a two-stage compression unit 1B in a hermetic container, and connects the first-stage compression unit 1A and the second-stage compression unit 1B. An intercooler 1C is provided on the refrigerant pipe.

  Further, as described above, the refrigerant introduction pipe 6 can introduce the gas refrigerant separated by the gas-liquid separator 4 between the intermediate pressure portion of the compressor 1, that is, between the intermediate cooler 1C and the two-stage compression portion 1B. Connected. The separated gas refrigerant is introduced into the intermediate pressure portion of the compressor 1 by the differential pressure in the refrigerant introduction pipe 6 as indicated by a broken line arrow. The compressor 1 is not limited to a two-stage compressor. For example, if the compressor 1 is a first-stage compressor, the refrigerant introduction pipe 6 may be returned to the intermediate pressure portion of the first-stage compressor. Further, a configuration in which a plurality of compressors are connected may be possible.

  Here, the gas-liquid separator 4 will be described with reference to FIG. FIG. 2 is a schematic sectional view of the gas-liquid separator 4.

  The gas-liquid separator 4 is provided with a container 80 formed of a substantially cylindrical hollow body, a first adsorption part 81A, and upper and lower parts of the first adsorption part 81A, and the adsorption part 81A is fixed in the container 80. Support members 81B and 81C, a second suction part 82A, and support members 82B and 82C provided above and below the second suction part 82A and for fixing the suction part 82A in the container 80. . The container 80 has a refrigerant pipe 4A for introducing the gas-liquid mixed refrigerant that has exited the radiator 2 on the side surface, and a gas refrigerant separated by the gas-liquid separator 4 flows out and compressed on the top surface. The refrigerant introduction pipe 6 connected to the intermediate pressure part of the machine 1 is attached to the bottom face, and the refrigerant pipe 4B from which the liquid refrigerant separated by the gas-liquid separator 4 flows out and connected to the three-way valve 91 is attached. Note that the separated liquid refrigerant is accumulated in a portion that is applied to the refrigerant pipe 4 </ b> B from the lower part in the container 80.

  The first and second adsorbing portions 81A and 82A are for adsorbing and removing moisture mixed in the refrigerant, and are filled with activated alumina, zeolite, or molecular sieve as a so-called desiccant. Further, the support members 81B, 81C, 82B, and 82C may be configured so that the adsorbing portions 81A and 82A can be prevented from flowing out and the refrigerant can be circulated. For example, a metal mesh or a resin mesh is used.

The refrigeration apparatus 30 of this embodiment has a small environmental load as a refrigerant, and carbon dioxide refrigerant (CO ₂ ), which is a natural refrigerant, is enclosed in consideration of flammability and toxicity. Further, as the oil as the lubricating oil of the compressor 2, for example, mineral oil (mineral oil), alkylbenzene oil, ether oil, ester oil, PAG (polyalkylene glycol), POE (polyol ester) and the like are used.

  Thus, since the refrigeration apparatus 30 uses carbon dioxide as a refrigerant, for example, when the outside air temperature becomes equal to or higher than the critical temperature of carbon dioxide (about + 31 ° C.), the high-pressure portion of the refrigeration cycle becomes a supercritical state. Thus, the refrigeration apparatus 30 is operated as a transcritical cycle.

  In this embodiment, in FIG. 1, the operation from the discharge side of the two-stage compression section 1B through the radiator 2 to the inlet of the third capillary tube 31 is operated as the high-pressure section of the refrigeration cycle of the refrigeration apparatus 30. From the discharge side of the compression unit 1A to the suction port of the two-stage compression unit 1B through the intermediate cooler 1C, from the outlet of the third capillary tube 31 to the suction port of the two-stage compression unit 1B through the gas-liquid separator 4, and three-way Up to the valve 91 is operated as an intermediate pressure part of the refrigeration cycle of the refrigeration apparatus 30. Then, from the outlet of the three-way valve 91 to the suction port of the first stage compression unit 1 </ b> A through the heat absorption means 8 and the first heat exchanger 15 is operated as a low pressure portion of the refrigeration cycle of the refrigeration apparatus 30.

  With the above configuration, the operation of the refrigeration apparatus 30 of the present embodiment will be described with reference to FIGS. 1 and 2. The refrigeration apparatus 30 is selected as necessary between a refrigeration operation mainly using the second capillary tube 13 and a refrigeration operation mainly using the first capillary tube 12.

  First, the freezing operation will be described. The freezing operation is an operation for cooling the freezer compartment 22 by causing the heat absorber 14 to function at a predetermined temperature (for example, around −26 ° C.).

  When the compressor 1 is operated in this embodiment, the refrigerant discharged from the compressor 1 is radiated by the radiator 2 and cooled. Thereafter, the refrigerant discharged from the radiator 2 reaches the third capillary tube 31 where it is decompressed to be in a gas-liquid mixed state (gas / liquid two-phase mixture), and from the refrigerant pipe 4A of the gas-liquid separator 4 It is introduced into the container 80 of the gas-liquid separator 4. In this container 80, the refrigerant is separated into a gas refrigerant and a liquid refrigerant, and the gas refrigerant passes through the second adsorbing portion 82A and flows through the refrigerant introduction pipe 6 as shown by the broken line arrow in FIG. After that, it is introduced into the intermediate pressure part of the compressor 1. On the other hand, the liquid refrigerant separated by the gas-liquid separator 4 passes through the first adsorbing portion 81A and reaches the heat absorbing means 8 through the first adsorbing portion 81A as indicated by a one-dot chain line arrow in FIG.

  Note that the refrigeration apparatus 30 is configured to perform two-stage expansion with the third capillary tube 31 and the first or second capillary tube 12, 13, so that the outlet side of the third capillary tube 31 and the first and second capillary tubes 12 and 13 between the inlet side, between the discharge side of the first-stage compression unit 1A of the compressor 1 and the suction side of the second-stage compression unit 1B, and in the refrigerant introduction pipe 6, It has become.

  Then, the liquid refrigerant is circulated to the second capillary tube 13 side by the three-way valve 91 of the heat absorption means 8, and this liquid refrigerant evaporates in the heat absorber 14 and absorbs heat from the surroundings, and then the first heat exchanger 15 The refrigerant in the vicinity of the three capillary tubes 31 is heated by the heat effect and returned to the suction port of the compressor 1. In the freezing operation, the control device 26 switches the switching damper 25 so that the cold air flows to the duct 58A side, so that the freezer compartment 22 is cooled.

  Next, the refrigeration operation will be described. This refrigeration operation is an operation in which the above-described heat absorber 14 is caused to function at a higher temperature (for example, around −5 ° C.) than during the refrigeration operation to cool the refrigeration chamber 21 intensively.

  During the refrigeration operation, the selected temperature zone in the heat absorbing means 8 is different from that during the refrigeration operation. That is, the liquid refrigerant exiting the gas-liquid separator 4 is circulated to the first capillary tube 12 side by the three-way valve 91 of the heat absorbing means 8 and then evaporated by the heat absorber 14 to absorb heat from the surroundings. During the refrigeration operation, the switching damper 25 is switched by the control device 26 so that cold air flows through the duct 57A, so that the refrigeration chamber 21 is cooled. In the refrigeration apparatus 30 of the present embodiment, the refrigeration cycle as described above is formed during the refrigeration operation and during the refrigeration operation.

  In the refrigeration apparatus 30, the gas refrigerant separated by the gas-liquid separator 4 cannot be used for cooling even if it is circulated to the heat absorption means 8, and this is sucked into the first stage compression unit 1A. Returning to the mouth reduces the compression efficiency of the compressor 1.

  Therefore, in this embodiment, the gas refrigerant separated by the gas-liquid separator 4 is introduced between the intermediate pressure portion of the compressor 1, that is, between the intermediate cooler 1C and the two-stage compression portion 1B. The compression efficiency in 1 can be improved. In particular, in the present embodiment, since the carbon dioxide refrigerant is sealed in the refrigerant circuit, in the ratio of gas and liquid separated by the gas-liquid separator 4, the gas content is larger than that of the fluorocarbon refrigerant, By introducing such a large amount of gas into the intermediate pressure portion of the compressor 1, higher efficiency can be improved.

  Further, in the present embodiment, as described above, the first and second adsorption portions 81A and 82A as the desiccant are provided in the container 80 of the gas-liquid separator 4, so that the gas-liquid separator 4 is a dryer integrated type. Since it is structured, moisture in the refrigerant can be adsorbed and removed by the gas-liquid separator 4 without providing a separate dryer in the refrigeration cycle as in the prior art, and freezing in the piping is prevented. In addition, the number of parts and the cost can be reduced.

  The refrigeration apparatus 30 uses carbon dioxide as the refrigerant. When carbon dioxide is used as the refrigerant in this way, the third capillary tube is connected from the high pressure side of the refrigeration cycle, in this embodiment from the discharge side of the compressor 1. The distance up to the inlet side of 31 is very high compared to conventional HFC (hydrofluorocarbon) refrigerant or HC (hydrocarbon) refrigerant. When a dryer is placed in this high pressure section, pressure resistance is required. However, in this embodiment, since the dryer-integrated gas-liquid separator 4 is disposed in the intermediate pressure portion, the pressure resistance of the container 80 can be suppressed, and the desiccant using a high-temperature and high-pressure refrigerant. Crushing of the (adsorption part) can be prevented. Further, in the refrigeration apparatus 30, gas refrigerant and liquid refrigerant pass through the first and second adsorption portions 81A and 82A of the gas-liquid separator 4, so that the rectifying action in these adsorption portions causes the gas / liquid separator 4 The liquid level in the liquid pool portion is easily stabilized.

  In the above description, the gas-liquid separator 4 shown in FIG. 2 has been described as the gas-liquid separator. However, the structures shown in FIGS. 3 and 4 are also applicable.

  FIG. 3 is a schematic sectional view of a gas-liquid separator 4-2 having another structure. This case is different from the gas-liquid separator 4 in that the second adsorption portion 82A and the support members 82B and 82C are not provided. FIG. 4 is a schematic cross-sectional view of a gas-liquid separator 4-3 having still another structure. This case is different from the gas-liquid separator 4 in that the first adsorption portion 81A and the support members 81B and 81C are not provided. Needless to say, these gas-liquid separators 4-2 and 4-3 can be reduced in cost as compared with the gas-liquid separator 4 and are effective depending on the use state and use conditions.

  Next, an application example of the refrigeration apparatus 30 of this embodiment to a refrigerator will be described with reference to FIG. FIG. 5 shows a schematic configuration diagram of a refrigerator provided with the refrigeration apparatus 30.

The refrigerator 40 includes a refrigeration room 41 in the upper stage and a freezing room 42 in the lower stage. An interior partition wall 43 is provided at the back of the freezer compartment 42, and the above-described heat absorber 14 is installed in the air passage 44 partitioned by the interior partition wall 43. A first switching damper 45 is disposed at the inlet A of the air passage 44, and the first switching damper 45 is located between a position (broken line position) for closing the inlet A of the air path 44 and a position (solid line position) for opening. Be switched between. Further, when the back side air passage 46 is formed in the back wall 47 of the refrigerator 40 and the first switching damper 45 is switched to the position of the broken line, the entrance of the air passage 44 is connected via the back side air passage 46. A communicates with the refrigerator compartment 41. A fan 48 and a second switching damper 49 are disposed at the outlet B of the air passage 44, and the second switching damper 49 closes the outlet B of the air passage 44 (broken line position) and opens ( The second switching damper 49 closes the opening 51 of the intermediate partition wall 50 at this solid line position.

  With the above configuration, during the refrigeration operation, the first switching damper 45 is set to a position where the inlet A of the air path 44 is opened (solid line position), and the second switching damper 49 is set to a position where the outlet B of the air path 44 is opened (solid line position). As a result, the air in the freezer compartment 42 is circulated and cooled by the heat absorber 14. Further, during the refrigeration operation, the first switching damper 45 is set to a position (broken line position) where the inlet A of the air passage 44 is closed, and the second switching damper 49 is set to a position (broken line position) where the outlet B of the air path 44 is closed. The air in the refrigerator compartment 41 is circulated through the back side air passage 46 and cooled by the heat absorber 14.

  Next, another embodiment of the present invention will be described with reference to FIG. FIG. 6 shows a refrigerant circuit diagram of the refrigeration apparatus 50 in this case. In the present embodiment, the same reference numerals as those in the first embodiment have the same or similar functions or effects. In this embodiment, when compared with the first embodiment, instead of the heat absorption means 8, the first heat absorption means 10 and the second heat absorption means 11 provided in parallel to the outlet side of the three-way valve 91 are provided. Is different.

  The first heat absorbing means 10 includes a first capillary tube 12 and a first heat absorber 57 provided in series with the first capillary tube 12. The second heat absorbing means 11 includes a second capillary tube 13, a second heat absorber 58 provided in series with the second capillary tube 13, and a check valve 52. And after the refrigerant | coolant piping of the exit side of the 1st and 2nd heat absorption means 10 and 11 merges at the junction 9B, the 1st heat exchanger 15 and the non-return valve like the refrigeration apparatus 30 of the said Example 1 are combined. 53 and connected to the suction port of the compressor 1. Moreover, the 1st heat absorption means 10 and the 2nd heat absorption means 11 function in a mutually different temperature range selectively.

  As described above, since the refrigerating apparatus 50 of the present embodiment includes the first and second heat absorbing means 10 and 11, the heat sinks 57 and 58 connect the refrigerator compartment 21 and the freezer compartment 22 with the ducts 57A and 58A, respectively. It is possible to selectively cool, and in a freezing operation and a refrigerating operation having different temperature ranges, a heat absorber suitable for the temperature can be used, and an improvement in operating efficiency of each operation can be expected.

  Next, an application example of the refrigeration apparatus 50 of this embodiment to a refrigerator will be described with reference to FIG.

  FIG. 7 shows a schematic configuration diagram of a refrigerator provided with the refrigeration apparatus 50 of the present embodiment. The refrigerator 40 includes a refrigeration room 41 in the upper stage and a freezing room 42 in the lower stage. And the interior partition walls 61 and 62 are provided in the inner part of each chamber 41 and 42, respectively, In the air channel 44 partitioned by this interior partition walls 61 and 62, the heat absorber 57, 58 and fans 63 and 64 are installed. In this configuration, the first heat absorbing means 10 and the second heat absorbing means 11 are switched in accordance with the thermo-ON and the thermo-OFF of the refrigeration operation and the freezing operation, the refrigerant is caused to flow through one of the heat absorbers 57 and 58, and the corresponding fan 63 , 64 are driven. When the refrigerant flows through the heat absorber 57, cold air is supplied to the refrigerating chamber 41, and when the refrigerant flows through the heat absorber 58, cold air is supplied to the freezer chamber 42.

  As described above, since the refrigerator 40 of the present embodiment includes the refrigeration apparatus 50 as described above, high cooling performance and high-efficiency operation are possible.

  Next, still another embodiment of the present invention will be described with reference to FIG. FIG. 8 shows a refrigerant circuit diagram of the refrigeration apparatus 70 in this case. In FIG. 8, the same reference numerals as those in the first and second embodiments have the same or similar functions or effects. The refrigeration apparatus 70 of the present embodiment is provided with third and fourth heat absorption means 10B and 11B instead of the first and second heat absorption means 10 and 11 when compared with the second embodiment. Is different.

  The third heat absorbing means 10B includes a first capillary tube 12 through which the refrigerant from the branch point 9C flows, a first expansion valve 65 provided in series with the first capillary tube 12, a refrigeration heat absorber 57, And a first heat exchanger 17 provided so that heat can be exchanged between the refrigerant discharged from the heat absorber 57 and the refrigerant in the vicinity of the first capillary tube 12. The fourth heat absorbing means 11B is provided in parallel with the third heat absorbing means 10B, and the decompressor 3, the gas-liquid separator 4, and the second capillary through which the refrigerant from the gas-liquid separator 4 flows. A tube 13, a second expansion valve 66 provided in series with the second capillary tube 13, a refrigeration heat absorber 58, a refrigerant discharged from the heat absorber 58, and a refrigerant in the vicinity of the second capillary tube 13. And a second heat exchanger 18 provided so as to be capable of heat exchange. A check valve 52 is provided between the outlet side of the heat absorber 58 and the second heat exchanger 18.

  Further, the third heat absorbing means 10B and the fourth heat absorbing means 11B function in different temperature ranges selectively, and the refrigerant pipe from the radiator 2 branches at the branch point 9C, and one of them is The third endothermic means 10B and the other end are provided in parallel as the fourth endothermic means 11B, and are joined again at the junction 9D before the suction port of the compressor 1.

  Here, the decompressor 3 is configured so that the degree of throttling is variable. By changing the degree of throttling, the refrigerant is reduced to a predetermined pressure before reaching the gas-liquid separator 4 and introduced into the gas-liquid separator 4, whereby the gas and liquid in the gas-liquid separator 4 are reduced. It becomes possible to change the ratio. The first expansion valve 65 and the second expansion valve 66 are also configured so that the degree of throttling is variable as in the decompressor 3.

  Since the third and fourth heat absorbing means 10B and 11B have the above-described configuration, for example, when the decompressor 3 is fully closed and the first expansion valve 65 is opened, the first capillary tube 12 side, that is, When the refrigerant flows only through the third heat absorbing means 10B, and conversely, the first expansion valve 65 is fully closed and the decompressor 3 and the second expansion valve 66 are opened, the second capillary tube side, that is, the first The refrigerant flows only through the four heat absorbing means 11B.

  Here, the refrigerant having passed through the heat absorber 57 passes through the first heat exchanger 17 installed in the vicinity of the first capillary tube 12 described above, and the refrigerant in the vicinity of the first capillary tube 12 in the first heat exchanger 17. After the heat exchange, the air is returned to the suction port of the compressor 1. The refrigerant that has passed through the heat absorber 58 passes through the check valve 52, passes through the second heat exchanger 18 installed in the vicinity of the second capillary tube 13 described above, and then passes through the second heat exchanger 18. After exchanging heat with the refrigerant in the vicinity of the capillary tube 13, the refrigerant is returned to the suction port of the compressor 1.

  Also in this embodiment, the gas refrigerant separated by the gas-liquid separator 4 cannot be used for cooling even if it is circulated through the fourth heat absorbing means 11B such as the second capillary tube 13 or the like. Returning this to the suction of the first-stage compression unit 1A reduces the compression efficiency in the compressor 1. Therefore, since the gas refrigerant separated by the gas-liquid separator 4 is introduced between the intermediate pressure portion of the compressor 1, that is, between the intermediate cooler 1C and the two-stage compression portion 1B, the compression efficiency in the compressor 1 is improved. Can be made.

  Here, since the refrigeration apparatus 70 is configured to circulate the refrigerant to the third heat absorption means 10B during the refrigeration operation, the refrigerant that introduces the gas refrigerant separated by the gas-liquid separator 4 into the intermediate pressure portion of the compressor 1 The function of the introduction pipe 6 cannot be used. However, during this refrigeration operation, the amount of gas refrigerant generated in the gas-liquid separator 4 is smaller than that during the refrigeration operation. Therefore, even if the operations of the decompressor 3 and the refrigerant introduction pipe 6 are stopped, the reduction in operating efficiency is reduced. Is suppressed.

  The refrigeration apparatus 70 of the present embodiment can be applied to a refrigerator, similarly to the refrigeration apparatus 50 of the second embodiment.

  A fourth embodiment of the present invention will be described with reference to FIG. FIG. 9 shows a refrigerant circuit diagram of the refrigeration apparatus 90 in this case. In FIG. 9, the same reference numerals as those in the above-described embodiments denote the same or similar functions or effects. The refrigeration apparatus 90 of the present embodiment includes a dryer 95 in the refrigerant pipe 4C between the outlet side of the third capillary tube 31 and the inlet side of the gas-liquid separator 4 when compared with the first embodiment. Is different.

  The dryer 95 is provided with an adsorbing portion as a moisture removing means in the refrigeration cycle inside a container formed of a substantially cylindrical hollow body. As this adsorbing portion, activated alumina, zeolite, molecular sieve, or the like as a desiccant enclosed in the gas-liquid separator 4 is used.

  As described above, since the refrigeration apparatus 90 includes the dryer 95, it is possible to apply the gas-liquid separator 4-4 having the structure shown in FIG.

  FIG. 10 is a schematic sectional view of the gas-liquid separator 4-4. This gas-liquid separator 4-4 is different from the gas-liquid separators 4, 4-1, 4-2 and 4-3 in that it does not have an adsorbing portion in the sealed container 80, Thereby, the cost of a gas-liquid separator can be reduced.

  As described above, according to the present embodiment, since carbon dioxide is used as the refrigerant, the high-pressure portion of the compression refrigeration cycle is compared with a conventional HFC (hydrofluorocarbon) refrigerant or HC (hydrocarbon) refrigerant. Although the pressure is extremely high, the refrigeration apparatus 90 of the present embodiment is configured to include the third capillary tube 31 to form a two-stage expansion cycle, and to include the dryer 95 in the intermediate pressure portion of the refrigeration cycle. The desiccant can be prevented from being crushed by the high-pressure refrigerant, and moisture in the refrigerant can be removed.

  In the refrigeration apparatus 90 of the present embodiment, the gas-liquid separators 4, 4-1, 4-2 and 4-3 can be applied instead of the gas-liquid separator 4-4. In this case, although there is a problem such as an increase in cost, it goes without saying that the water removal capability of the refrigeration cycle is improved and becomes effective depending on the use state and use conditions of the refrigeration apparatus 90.

  Moreover, the freezing apparatus 90 of a present Example is applicable to a refrigerator similarly to the said each Example.

  Although the present invention has been described with the above embodiments, the present invention is not limited to this, and various modifications can be made. For example, in each of the above embodiments, the carbon dioxide refrigerant is enclosed in the refrigerant circuit. However, the present invention is not limited to this, and the present invention can be applied to other refrigerant-filled refrigerants.

  In each of the above embodiments, the capillary tube can be changed to an expansion valve, and the expansion valve can be changed to a capillary tube as necessary.

It is a refrigerant circuit figure which shows one Example of the freezing apparatus of this invention. It is a schematic sectional drawing which shows an example of the gas-liquid separator of this invention. It is a schematic sectional drawing which shows the other example of the gas-liquid separator of this invention. It is a schematic sectional drawing which shows the other example of the gas-liquid separator of this invention. It is a schematic block diagram which shows the example of application to the refrigerator of the freezing apparatus of one Example of this invention. It is a refrigerant circuit figure which shows the freezing apparatus of the other Example of this invention. It is a schematic block diagram which shows the example of application to the refrigerator of the freezing apparatus of the other Example of this invention. It is a refrigerant circuit figure which shows the freezing apparatus of the further another Example of this invention. It is a refrigerant circuit figure which shows the freezing apparatus of the 4th Example of this invention. It is a schematic sectional drawing which shows the gas-liquid separator applicable to the freezing apparatus of the 4th Example of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Compressor 2 Radiator 3 Pressure reducer 4 Gas-liquid separator 6 Refrigerant introduction pipe 7, 52, 53 Check valve 8, 10, 10B, 11B Heat absorption means 12, 13, 31 Capillary tube 14, 57, 58 Heat absorber 21 , 41 Refrigeration room 22, 42 Freezer room 30, 50, 70, 90 Refrigeration device 40 Refrigerator 48, 63, 64 Fan 65, 66 Expansion valve 80 Container 81A, 82A Adsorption part 91 Three-way valve 95 Dryer

Claims (7)

A compressor, a radiator connected to the discharge side of the compressor, a first decompression means connected to the outlet side of the radiator, and a second connected in series with the first decompression means In a refrigeration apparatus including a refrigeration cycle including a decompression unit and a heat absorber connected to an outlet side of the second decompression unit,
A refrigerating apparatus comprising an adsorption means for adsorbing moisture in the refrigerant between an outlet side of the first decompression means and an inlet side of the second decompression means. A container in which a mixed refrigerant of gas and liquid is introduced and gas and liquid are separated inside, an introduction pipe for introducing the refrigerant into the container, and a gas refrigerant separated in the container flows out. 1 outlet pipe, and a second outlet pipe through which the liquid refrigerant separated in the container flows out,
A gas-liquid separator comprising an adsorption part for adsorbing moisture in the refrigerant in the container. A compressor, a radiator connected to the discharge side of the compressor, a first decompression means connected to the outlet side of the radiator, and a second connected in series with the first decompression means In a refrigeration apparatus including a refrigeration cycle including a decompression unit and a heat absorber connected to an outlet side of the second decompression unit,
A refrigerating apparatus comprising the gas-liquid separator according to claim 2 between an outlet side of the first pressure reducing means and an inlet side of the second pressure reducing means. The compressor has an intermediate pressure section;
The refrigeration apparatus according to claim 3, wherein a first outlet pipe of the gas-liquid separator is connected to the intermediate pressure section.   5. The refrigeration apparatus according to claim 1, wherein the high-pressure portion of the refrigeration cycle is operated at a supercritical pressure.   The refrigeration apparatus according to any one of claims 1, 3, 4 and 5, wherein carbon dioxide is used as the refrigerant. A refrigerator comprising the refrigeration apparatus according to any one of claims 1, 3, 4, 5, and 6.

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