JP2008057941A - Refrigerant cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerant cycle device capable of properly cooling internal atmosphere of a housing by inhibiting occurrence of defective distribution. <P>SOLUTION: The refrigerant cycle device 10 for cooling the internal atmosphere in commodity storages by circulating a refrigerant to a refrigerant circulation circuit comprises: a compressor 11 for compressing a refrigerant; a gas cooler 12 for allowing the refrigerant to radiate heat; evaporators 15 respectively disposed in the plurality of commodity storages 5a, 5b, 5c to evaporate the supplied refrigerant; an ejector 13 sucking the refrigerant evaporated by the evaporators 15 by decompressing the refrigerant from the gas cooler 12, mixing the refrigerant with the decompressed refrigerant, and discharging the same, and a gas-liquid separator 14 separating the mixed refrigerant discharged from the ejector 13 into a gas refrigerant and a liquid refrigerant, delivering the gas refrigerant to the compressor 11, and delivering the liquid refrigerant to the evaporators 15. The gas-liquid separator 14 delivers the liquid refrigerant toward each of the evaporators 15 in a distributed manner. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a refrigerant cycle device, and more particularly, to a refrigerant cycle device that cools the internal atmosphere of a heat insulating housing in, for example, a vending machine, a refrigerator, a freezing / refrigeration showcase, or a beverage dispenser.

  Conventionally, for example, a refrigerant cycle device that cools the internal atmosphere of a heat insulating housing in a vending machine, a refrigerator, a freezer / refrigerator showcase, a beverage dispenser, etc., includes a compressor, a radiator, an evaporator, an ejector, and a gas-liquid separator. It is prepared for.

  The compressor compresses the supplied refrigerant. The radiator radiates heat from the high-pressure refrigerant compressed by the compressor. For example, the evaporator is disposed inside a heat insulating housing such as a commodity container. When there are a plurality of heat insulating housings, the evaporator is disposed for each heat insulating housing. This evaporator evaporates the supplied refrigerant.

  The ejector uses the energy generated by depressurizing the high-pressure refrigerant (high-pressure refrigerant) supplied from the radiator to suck the low-pressure refrigerant (low-pressure refrigerant) evaporated in the evaporator, and the sucked low-pressure refrigerant is used as the high-pressure refrigerant. And the pressure of the low-pressure refrigerant is increased and then discharged. The gas-liquid separator separates the mixed refrigerant supplied from the ejector into a gas refrigerant and a liquid refrigerant, sends the gas refrigerant to the compressor, and sends the liquid refrigerant to the evaporator.

  The compressor, the radiator, the ejector, and the gas-liquid separator are sequentially connected in a ring shape, and an evaporator is provided between the low-pressure refrigerant inlet of the ejector and the liquid refrigerant outlet of the gas-liquid separator. A refrigerant circulation circuit is configured, and the refrigerant is circulated through the refrigerant circulation circuit. Thereby, the peripheral region of the evaporator is cooled in order to absorb heat as the refrigerant evaporates. As a result, the internal atmosphere of the heat insulating housing is cooled. Here, carbon dioxide is used as the refrigerant from the viewpoint of the global environment and the like.

  In such a refrigerant cycle device, there is known one that distributes liquid refrigerant sent from a gas-liquid separator through distribution pipes and then sends the refrigerant to each evaporator (see, for example, Patent Document 1).

JP 2002-22295 A

  By the way, it is known that the liquid refrigerant separated by the gas-liquid separator is in contact with the wall surface of the pipe when flowing toward the evaporator, causing a pressure loss and foaming to become a gas-liquid two-phase flow. ing. The refrigerant that becomes such a gas-liquid two-phase flow has a low flow rate because the amount of foaming is not so large. Therefore, if such refrigerant is distributed in the conventional distribution pipe, Only the liquid refrigerant flows, and the refrigerant containing the gas flows through the relatively upper pipe, which may cause a distribution failure. When such distribution failure occurs, the circulation amount of the refrigerant flowing through the evaporator connected to the upper pipe is smaller than the circulation amount of the refrigerant flowing through the evaporator connected to the lower pipe. As a result, the cooling capacity is reduced.

  In view of the above circumstances, an object of the present invention is to provide a refrigerant cycle device that can suppress the occurrence of poor distribution and can cool the internal atmosphere of a housing satisfactorily.

  In order to achieve the above object, a refrigerant cycle device according to claim 1 of the present invention includes a compressor that compresses a supplied refrigerant, a radiator that dissipates high-pressure refrigerant compressed by the compressor, and a plurality of radiators. An evaporator that is individually disposed in the casing and evaporates the supplied refrigerant, and depressurizes the high-pressure refrigerant supplied from the radiator, thereby sucking the low-pressure refrigerant evaporated in the evaporator, and An ejector that mixes and discharges the refrigerant with a decompressed refrigerant, and separates the mixed refrigerant discharged from the ejector into a gas refrigerant and a liquid refrigerant, and sends the gas refrigerant to the compressor, while the liquid refrigerant is sent to the evaporator In the refrigerant cycle device that cools the internal atmosphere in the casing by circulating the refrigerant in a refrigerant circulation circuit including a gas-liquid separator that is sent to the gas-liquid separator, the gas-liquid separator is connected to each evaporator. Only in that wherein the sending in a manner that distributes the liquid refrigerant.

  The refrigerant cycle device according to claim 2 of the present invention is the refrigerant cycle device according to claim 1, wherein the gas-liquid separator has a liquid refrigerant pipe for sending the liquid refrigerant toward each evaporator. It is arranged by being inserted in the separator.

  A refrigerant cycle device according to a third aspect of the present invention is the refrigerant cycle device according to the first or second aspect, wherein each refrigerant inflow portion of the liquid refrigerant pipe is a center of a horizontal section of the gas-liquid separator. It is characterized by being installed at a position where the distance from the same is the same.

  The refrigerant cycle device according to a fourth aspect of the present invention is the refrigerant cycle device according to any one of the first to third aspects, wherein the inner diameter of each of the liquid refrigerant pipes is set to a size of a cooling load of a corresponding casing. It is characterized in that it is enlarged in response.

  According to the present invention, since the gas-liquid separator delivers the liquid refrigerant to the respective evaporators in such a manner that the liquid refrigerant is distributed, only the liquid refrigerant flows through one evaporator and the gas is supplied to the other evaporator. Generation | occurrence | production of the distribution defect which the containing refrigerant | coolant flows can be suppressed, and, thereby, the circulation amount of the refrigerant | coolant which flows through one of evaporators becomes small, and does not cause the fall of cooling capacity. Therefore, there is an effect that the internal atmosphere of the product storage can be cooled well.

  Exemplary embodiments of a refrigerant cycle device according to the present invention will be explained below in detail with reference to the accompanying drawings. In the following, for convenience of explanation, the refrigerant cycle device will be described as being applied to a vending machine.

  1 and 2 schematically show a vending machine to which a refrigerant cycle device according to an embodiment of the present invention is applied, FIG. 1 is a front sectional view, and FIG. 2 is a sectional view. It is a side view. 1 and 2, the vending machine includes a main body cabinet 1.

  The main body cabinet 1 is formed as a rectangular heat insulator having an open front surface. The main body cabinet 1 is provided with an outer door 2 and inner doors 3a and 3b on the front surface thereof, and for example, three independent commodity containers 5a and 5b partitioned inside by two heat insulating partition plates 4a and 4b. , 5c are arranged side by side. More specifically, the outer door 2 is for opening and closing the front opening of the main body cabinet 1, and the inner doors 3a and 3b are for opening and closing the front surfaces of the product containers 5a, 5b and 5c. is there. The inner doors 3a and 3b are divided into upper and lower parts, and the upper door 3a opens and closes when a product is replenished. The product containers 5a, 5b, 5c are for storing the product W such as a canned beverage or a beverage containing a plastic bottle while maintaining the desired temperature.

  The product storage 5a, 5b, 5c is provided with a product storage rack 6, a carry-out mechanism 7 and a product carry-out shooter 8, respectively. The product storage rack 6 is for storing the products W in a manner of being arranged along the vertical direction. The carry-out mechanism 7 is provided at the lower part of the product storage rack 6, and is used to carry out the products W at the lowest level of the product group stored in the product storage rack 6 one by one. The product carry-out shooter 8 is for guiding the product W carried out from the carry-out mechanism 7 to the product take-out port 3c.

  A refrigerant cycle unit 10a is disposed in the machine room 9 inside the main body cabinet 1 and outside the commodity storages 5a, 5b, 5c. Although the refrigerant cycle unit 10a will be described in detail later, the refrigerant circulation circuit together with the evaporators 15a, 15b, and 15c (hereinafter also simply referred to as the evaporator 15) disposed in the respective product storages 5a, 5b, and 5c. Is formed to constitute the refrigerant cycle device 10.

  FIG. 3 is a conceptual diagram conceptually showing the refrigerant cycle device (refrigerant cycle device in the embodiment of the present invention) shown in FIGS. 1 and 2. In FIG. 3, the refrigerant cycle device 10 includes a refrigerant circulation circuit, and the refrigerant circulation circuit includes a compressor 11, a gas cooler (heat radiator) 12, an ejector 13, and a gas-liquid separator 14. The evaporators 15a, 15b, and 15c are appropriately connected. In the refrigerant cycle device 10, carbon dioxide, which has nonflammability, safety and noncorrosiveness and has little influence on the ozone layer, is used as a refrigerant.

  The compressor 11 compresses refrigerant (carbon dioxide) into a high temperature and high pressure state. The compressor 11 is a two-stage compressor that performs a compression operation in two steps. More specifically, the compressor 11 includes a first compressor 111 that performs a first compression operation and a second compressor 112 that performs a second compression operation, and an intermediate heat exchanger therebetween. 113 is provided. The intermediate heat exchanger 113 cools, that is, releases heat, the refrigerant compressed by the first compression operation by the first compressor 111 and sends the refrigerant to the second compressor 112. Here, the intermediate heat exchanger 113 uses a fin tube type composed of, for example, a metal pipe such as stainless steel and an aluminum fin. In addition, a blower fan F1 for air volume adjustment is installed in the vicinity of the intermediate heat exchanger 113.

  Thus, the compressor 11 can compress the refrigerant into a desired high temperature and high pressure state with low power consumption by executing the compression operation twice through the intermediate heat exchanger 113. In the present embodiment, the refrigerant is compressed to about 4.9 MPa by the first compression by the first compressor 111, and the refrigerant is compressed to about 9.8 MPa by the second compression by the second compressor 112. To do.

  Here, as the compressor 11, a reciprocating compressor, a rotary compressor, a scroll compressor, or an inverter compressor capable of adjusting the compression capacity thereof can be applied. And what is necessary is just to apply suitably the compressor corresponding to the object etc. which arrange | position the refrigerant | coolant cycle apparatus 10, an environment, or the cost which the whole apparatus requires.

  The gas cooler 12 dissipates heat from the refrigerant compressed by the compressor 11 into a high-temperature and high-pressure state, that is, a high-pressure refrigerant. The gas cooler 12 in the present embodiment uses a fin tube type composed of a metal pipe such as copper and aluminum fins, for example. Moreover, the gas cooler 12 has a volume substantially equal to that of the intermediate heat exchanger 113 described above. In the vicinity of the gas cooler 12, an outside fan F2 for air volume adjustment is installed.

  As will be described in detail later, the ejector 13 sucks out the low-pressure refrigerant (low-pressure refrigerant) evaporated by the evaporator 15 by depressurizing the high-pressure refrigerant radiated by the gas cooler 12, and draws the sucked low-pressure refrigerant from the gas cooler 12. Are mixed with a high-pressure refrigerant and pressurized, and then discharged through a mixed refrigerant pipe. As shown in FIG. 4, the ejector 13 in the present embodiment is a two-phase flow ejector, and includes a nozzle part 131, a mixing part 132, and a diffuser part 133.

  The nozzle part 131 is a part that accelerates the high-pressure refrigerant from the gas cooler 12 sucked through the high-pressure refrigerant inlet 134 by reducing the pressure. By accelerating the high-pressure refrigerant in this way, the low-pressure refrigerant evaporated by the evaporator 15 can be sucked through the refrigerant inlet 135. The nozzle portion 131 is provided with a nozzle valve 131a. The nozzle valve 131a is a valve body for adjusting the nozzle diameter for depressurizing the high-pressure refrigerant. That is, the opening degree of the ejector 13 can be adjusted by driving the nozzle valve 131a.

  The mixing unit 132 is a part that mixes the high-pressure refrigerant accelerated by the nozzle unit 131 and the low-pressure refrigerant sucked through the refrigerant suction port 135.

  The diffuser unit 133 is a part that pressurizes the refrigerant (mixed refrigerant) mixed in the mixing unit 132. The mixed refrigerant whose pressure has been increased is discharged toward the gas-liquid separator 14 through the mixed refrigerant pipe 21.

  The gas-liquid separator 14 separates the mixed refrigerant discharged from the ejector 13 and passed through the mixed refrigerant pipe 21 into a gas refrigerant and a liquid refrigerant, and the separated gas refrigerant is compressed through the gas refrigerant pipe 22 into the compressor 11 ( While being sent to the first compressor 111), the separated liquid refrigerant is sent to the evaporators 15a, 15b and 15c through the liquid refrigerant pipes 23a, 23b and 23c. The configuration of the gas-liquid separator 14 will be described.

  As shown in FIGS. 5 and 6, the gas-liquid separator 14 has a cylindrical shape in which an upper part and a lower part have a spherical shape, and a mixed refrigerant pipe 21 is disposed in the upper part. A gas refrigerant pipe 22 is provided in the portion, and a plurality (for example, three) of liquid refrigerant pipes 23a, 23b, and 23c are provided at predetermined positions on the peripheral surface.

  More specifically, the mixed refrigerant pipe 21 is arranged in such a manner that it passes through the upper part of the gas-liquid separator 14 and extends on the central axis of the gas-liquid separator 14. The outflow portion of the refrigerant is located above the inside of the gas-liquid separator 14.

  The gas refrigerant pipe 22 is arranged in such a manner that it passes through the lower portion of the gas-liquid separator 14 and extends on the central axis of the gas-liquid separator 14, and the inflow portion of the gas refrigerant is the gas refrigerant. It is located inside the liquid separator 14. The position of the inflow portion is adjusted at a location where the gas refrigerant stays when the refrigerant stays inside the gas-liquid separator 14. The gas refrigerant pipe 22 is provided with an oil passage hole (not shown) at a position on the lowermost side of the portion extending inside the gas-liquid separator 14. The oil passage hole is a hole for allowing the refrigerating machine oil staying inside the gas-liquid separator 14 to pass through, as will be described in detail later.

  Each of the plurality of liquid refrigerant pipes 23a, 23b, and 23c is arranged in such a manner that each of the liquid refrigerant pipes 23a, 23b, and 23c is inserted through a predetermined portion in a lower region of the peripheral surface of the gas-liquid separator 14 and extends on the same horizontal plane. . As shown in FIG. 6, the inflow portions of these liquid refrigerant pipes 23 a, 23 b, and 23 c are below the inflow portion of the gas refrigerant pipe 22 and are substantially the same distance from the center of the cross section of the gas-liquid separator 14. It is installed at a position that is only apart. The position of the inflow portion is adjusted at a location where the liquid refrigerant stays inside the gas-liquid separator 14.

  A shielding plate 14 a is provided inside the gas-liquid separator 14. The shielding plate 14 a is provided above the internal space of the gas-liquid separator 14 and below the outflow portion of the mixed refrigerant pipe 21. Such a shielding plate 14 a is a type in which the mixed refrigerant ejected from the outflow portion of the mixed refrigerant pipe 21 through the mixed refrigerant pipe 21 collides. Although not clearly shown in the drawing, the shielding plate 14a is provided with a refrigerant passage penetrating along the vertical direction, and the mixed refrigerant ejected from the outflow portion of the mixed refrigerant pipe 21 collides with the shielding plate 14a. Then, it falls down inside the gas-liquid separator 14 through the refrigerant passage. Here, the refrigerant passage is provided at a position separated from the inflow portion of the gas refrigerant pipe 22 in order to prevent the refrigerant that has passed through the refrigerant passage from directly entering the inside of the gas refrigerant pipe 22. That is, it is provided at a position separated from the central axis of the gas-liquid separator 14.

  The evaporators 15a, 15b, and 15c evaporate the liquid refrigerant that has been discharged by the gas-liquid separator 14 and passed through the liquid refrigerant pipes 23a, 23b, and 23c. As the refrigerant evaporates, the surrounding areas of the evaporators 15a, 15b, and 15c are cooled as a result of heat being taken away. As the evaporators 15a, 15b, and 15c in the present embodiment, a fin tube type composed of a copper tube and an aluminum fin is used.

  As shown in FIG. 2, the evaporators 15 a, 15 b, and 15 c are provided inside the product containers 5 a, 5 b, and 5 c in order to cool the plurality of product containers 5 a, 5 b, and 5 c independently. It is arranged. In more detail, the evaporator 15a is arrange | positioned inside the goods storage 5a, the evaporator 15b is arrange | positioned inside the goods storage 5b, and the evaporator 15c is the goods storage 5c. Is disposed inside. The evaporator 15a is connected to the liquid refrigerant pipe 23a, the evaporator 15b is connected to the liquid refrigerant pipe 23b, and the evaporator 15c is connected to the liquid refrigerant pipe 23c. In addition, electromagnetic valves 16a, 16b, and 16c are provided in the liquid refrigerant pipes 23a, 23b, and 23c, respectively. Then, by selectively opening the electromagnetic valves 16a, 16b, 16c, the liquid refrigerant pipes 23a, 23b, 23c in which the electromagnetic valves 16a, 16b, 16c are disposed are opened, and the corresponding evaporator 15a , 15b, 15c, the refrigerant from the gas-liquid separator 14 is sent out. On the other hand, the paths on the outlet side of the respective evaporators 15a, 15b, 15c are gathered together and connected to the refrigerant suction port 135 of the ejector 13. Accordingly, the refrigerant evaporated in the evaporators 15a, 15b, and 15c reaches the ejector 13.

  In the vicinity of the evaporators 15a, 15b, and 15c in each of the merchandise containers 5a, 5b, and 5c, a heater H, an internal fan F, a circulation duct D, and the like are provided. The heater H is for heating the air (internal atmosphere) of the product storage 5a, 5b, 5c, that is, for heating the product W stored in the product storage rack 6. The internal blower fan F blows air (cold air) cooled by the evaporators 15a, 15b, 15c or air heated by the heater H (warm air), thereby cooling the evaporators 15a, 15b, 15c. Alternatively, high heat from the heater H is transferred to the product W. The air blown by the internal blower fan F is circulated through the circulation duct D.

  The refrigerant cycle device 10 having the above-described configuration can cool the internal atmosphere of the commodity storage 5a, 5b, 5c of the vending machine as follows. Here, it demonstrates as what cools the internal atmosphere of all the product storage 5a, 5b, 5c. In addition, the heater H arrange | positioned inside each goods storage 5a, 5b, 5c is an OFF state. The opening of the ejector 13 is adjusted to a predetermined size.

  The refrigerant in the refrigerant circuit is compressed by the compressor 11 in two steps. More specifically, the refrigerant is compressed (compressed to about 4.9 MPa) by the first compressor 111 and then sent to the intermediate heat exchanger 113. The refrigerant sent to the intermediate heat exchanger 113 dissipates heat in the intermediate heat exchanger 113 and is cooled. The refrigerant cooled by the intermediate heat exchanger 113 is sent again to the second compressor 112 and is compressed (compressed to about 9.8 MPa) by the second compressor 112 to be in a high temperature and high pressure state. In this case, the refrigeration oil sent together with the refrigerant from the second compressor 112 returns to the inlet side of the first compressor 111 by the oil separator.

  The high-temperature and high-pressure refrigerant is sent to the gas cooler 12 and is radiated and cooled by the gas cooler 12. The refrigerant (high-pressure refrigerant) cooled by the gas cooler 12 is sent to the ejector 13.

  The refrigerant (high-pressure refrigerant) sent to the ejector 13 enters the nozzle portion 131 through the high-pressure refrigerant inlet 134 and is accelerated by being decompressed. Thereby, the refrigerant (low-pressure refrigerant) that has passed through the evaporators 15a, 15b, and 15c is sucked through the refrigerant inlet 135. Then, in the mixing unit 132 of the ejector 13, the accelerated high-pressure refrigerant and the sucked low-pressure refrigerant are mixed to be a mixed refrigerant and reach the diffuser unit 133, and the mixed refrigerant is pressurized by the diffuser unit 133. After being discharged.

  The mixed refrigerant (low-pressure refrigerant) discharged from the ejector 13 is sent to the gas-liquid separator 14 through the mixed refrigerant pipe 21. More specifically, it is ejected from the outflow portion of the mixed refrigerant pipe 21 into the gas-liquid separator 14, collides with the shielding plate 14 a, and then falls downward through the refrigerant passage. The fallen mixed refrigerant is separated in phase from the bottom in the order of refrigeration oil, liquid refrigerant, and gaseous refrigerant due to the difference in density. Then, the refrigeration oil enters the gas refrigerant pipe 22 through the oil passage hole, and is sent out toward the compressor 11 (first compressor 111) through the pipe. Further, the gas refrigerant enters the gas refrigerant pipe 22 from the inflow portion of the gas refrigerant pipe 22 and is sent out toward the compressor 11 (first compressor 111) through the pipe.

  On the other hand, the separated liquid refrigerant enters the liquid refrigerant pipes 23a, 23b, and 23c from the inflow portions of the liquid refrigerant pipes 23a, 23b, and 23c, and is sent to the evaporators 15a, 15b, and 15c through the respective pipes. Is done. The refrigerant sent to the evaporators 15a, 15b, and 15c evaporates by being given heat from the peripheral areas of the evaporators 15a, 15b, and 15c. In other words, the surrounding areas of the evaporators 15a, 15b, and 15c are cooled by taking heat away as the refrigerant evaporates to generate cold air. The generated cold air is blown out as indicated by the arrow in FIG. 2 by the action of the internal blower fan F, thereby cooling the internal atmosphere of the product containers 5a, 5b, 5c. When the internal atmosphere of the product storage 5a, 5b, 5c is cooled in this way, the product W stored in the product storage rack 6 arranged inside the product storage 5a, 5b, 5c is a desired product. It will be cooled to a temperature state (eg, about 5 ° C.).

  The refrigerant evaporated in the evaporators 15a, 15b, and 15c is discharged from the evaporators 15a, 15b, and 15c by the suction force generated when the high-pressure refrigerant is depressurized and accelerated in the ejector 13, and the refrigerant suction port of the ejector 13 is discharged. To 135. In this way, the refrigerant repeats the cycle of circulating through the refrigerant circuit.

  In the refrigerant cycle device 10 in the present embodiment as described above, the inflow portions of the respective liquid refrigerant pipes 23a, 23b, 23c connected to the evaporators 15a, 15b, 15c are inside the gas-liquid separator 14. It is arranged in an inserted manner. Therefore, the liquid refrigerant separated inside the gas-liquid separator 14 is distributed and sent to the liquid refrigerant pipes 23a, 23b, and 23c. In other words, the gas-liquid separator 14 sends out the liquid refrigerant toward the respective evaporators 15a, 15b, and 15c. In this way, in the gas separator, by sending out the liquid refrigerant toward the respective evaporators 15a, 15b, 15c, only the liquid refrigerant flows in one pipe, and the gas is sent to the other pipes. Generation | occurrence | production of the distribution defect which the containing refrigerant | coolant flows can be suppressed.

  Therefore, according to the refrigerant cycle device 10, since it is possible to suppress the occurrence of poor distribution, the circulation amount of the refrigerant flowing through any one of the evaporators 15a, 15b, and 15c is reduced and the cooling capacity is reduced. Without inviting, the internal atmosphere of the product containers 5a, 5b, 5c can be cooled well.

  Further, according to the refrigerant cycle device 10, the inflow portions of the liquid refrigerant pipes 23 a, 23 b, and 23 c are installed at positions separated from the center of the cross section of the gas-liquid separator 14 by substantially the same distance. A swirling flow is generated inside the liquid separator 14, and the liquid refrigerant and the refrigerating machine oil staying below the gas-liquid separator 14 are swirled so that the vicinity of the central axis inside the gas-liquid separator 14. And the vicinity of the wall surface are different in liquid level height, the mixing ratio of the liquid refrigerant and the gas refrigerant entering the liquid refrigerant pipes 23a, 23b, and 23c is almost the same. , 15b, 15c, the circulation amount of the refrigerant is reduced, and the cooling capacity is not reduced.

  In the refrigerant cycle apparatus according to the embodiment of the present invention as described above, a gas-liquid separator as shown in FIGS. 7 to 16 may be used. In the gas-liquid separator 14 ′ shown in FIGS. 7 and 8, the liquid refrigerant pipes 23 a, 23 b, 23 c are arranged in the vicinity of the central axis of the gas-liquid separator 14, and the gas refrigerant pipe 22 is arranged on the outer periphery thereof. Configured. Also in such a case, the inflow portions of the liquid refrigerant pipes 23a, 23b, and 23c are installed at positions that are separated from the center of the cross section of the gas-liquid separator 14 by substantially the same distance. Further, the gas refrigerant pipe 22 is bent so that the inflow portion of the gas refrigerant pipe 22 is not located immediately below the refrigerant passage provided in the shielding plate 14a. Even with such a configuration, it is possible to suppress the occurrence of poor distribution by sending the liquid refrigerant to the respective evaporators 15a, 15b, and 15c in such a manner that the liquid refrigerant is distributed. , 5c can be satisfactorily cooled, and even if a swirling flow is generated inside the gas-liquid separator 14, the cooling capacity is not reduced.

  The gas-liquid separator 141 shown in FIGS. 9 and 10 is configured by changing the diameters of the liquid refrigerant pipes 23a, 23b, and 23c in accordance with the volumes of the product containers 5a, 5b, and 5c, that is, the cooling load. It is. Also in such a case, the inflow portions of the liquid refrigerant pipes 23a, 23b, and 23c are installed at positions separated from the center of the cross section of the gas-liquid separator 14 by substantially the same distance. Even with such a configuration, it is possible to suppress the occurrence of poor distribution by sending the liquid refrigerant to the respective evaporators 15a, 15b, and 15c in such a manner that the liquid refrigerant is distributed. , 5c can be satisfactorily cooled, and even if a swirling flow is generated inside the gas-liquid separator 14, the cooling capacity is not reduced. Further, since the diameters of the liquid refrigerant pipes 23a, 23b, and 23c are changed according to the cooling load, it is possible to shorten the refrigerant time and increase the efficiency.

  The gas-liquid separator 142 shown in FIGS. 11 and 12 is configured by changing the diameters of the liquid refrigerant pipes 23a, 23b, and 23c according to the volumes of the product containers 5a, 5b, and 5c, that is, the cooling load. It is. The liquid refrigerant pipes 23a, 23b, and 23c are arranged so as to pass through the lower part of the gas-liquid separator 14, and the inflow parts are substantially the same distance from the center of the cross section of the gas-liquid separator 14. It is installed at a position that is only apart. Even with such a configuration, it is possible to suppress the occurrence of poor distribution by sending the liquid refrigerant to the respective evaporators 15a, 15b, and 15c in such a manner that the liquid refrigerant is distributed. , 5c can be satisfactorily cooled, and even if a swirling flow is generated inside the gas-liquid separator 14, the cooling capacity is not reduced. Further, since the diameters of the liquid refrigerant pipes 23a, 23b, and 23c are changed according to the cooling load, it is possible to shorten the refrigerant time and increase the efficiency.

  In the gas-liquid separator 143 shown in FIGS. 13 and 14, the liquid refrigerant pipes 23 a, 23 b, and 23 c are arranged in such a manner that the lower part of the gas-liquid separator 14 is inserted. Even with such a configuration, it is possible to suppress the occurrence of poor distribution by sending the liquid refrigerant to the respective evaporators 15a, 15b, and 15c in such a manner that the liquid refrigerant is distributed. , 5c can be cooled satisfactorily.

  In the gas-liquid separator 144 shown in FIGS. 15 and 16, the gas refrigerant pipe 22 and the liquid refrigerant pipes 23 a, 23 b, and 23 c are linearly arranged in such a manner that the lower part of the gas-liquid separator 14 is inserted. is there. Even with such a configuration, it is possible to suppress the occurrence of poor distribution by sending the liquid refrigerant to the respective evaporators 15a, 15b, and 15c in such a manner that the liquid refrigerant is distributed. , 5c can be cooled satisfactorily.

  As described above, the present invention is useful for cooling the internal atmosphere of a heat-insulating housing such as a commodity storage of a vending machine.

It is the front sectional view showing typically the vending machine to which the refrigerant cycle device in an embodiment of the invention was applied. 1 is a cross-sectional circumferential view schematically showing a vending machine to which a refrigerant cycle device according to an embodiment of the present invention is applied. It is the conceptual diagram which showed notionally the refrigerant cycle apparatus shown in FIG.1 and FIG.2. It is sectional drawing which showed the ejector shown in FIG. It is the side view which showed the gas-liquid separator shown in FIG. It is a figure from the arrow A shown in FIG. It is the side view which showed the modification of the gas-liquid separator in embodiment of this invention. It is a figure from the arrow A shown in FIG. It is the side view which showed the modification of the gas-liquid separator in embodiment of this invention. FIG. 10 is a view from an arrow A shown in FIG. 9. It is the side view which showed the modification of the gas-liquid separator in embodiment of this invention. It is a figure from the arrow A shown in FIG. It is the side view which showed the modification of the gas-liquid separator in embodiment of this invention. It is a figure from the arrow A shown in FIG. It is the side view which showed the modification of the gas-liquid separator in embodiment of this invention. It is a figure from the arrow A shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Refrigerating-cycle apparatus 11 Compressor 12 Gas cooler 13 Ejector 14 Gas-liquid separator 15 (15a, 15b, 15c) Evaporator 21 Mixed refrigerant | coolant piping 22 Gas refrigerant | coolant piping 23a, 23b, 23c Liquid refrigerant piping

Claims (4)

A compressor for compressing the supplied refrigerant;
A radiator that dissipates heat from the high-pressure refrigerant compressed by the compressor;
An evaporator that is individually disposed in a plurality of cases and evaporates the supplied refrigerant;
An ejector that sucks out the low-pressure refrigerant evaporated in the evaporator by depressurizing the high-pressure refrigerant supplied from the radiator, and mixes and discharges the low-pressure refrigerant with the decompressed refrigerant;
A refrigerant circulation circuit comprising: a gas-liquid separator that separates the mixed refrigerant discharged from the ejector into a gas refrigerant and a liquid refrigerant, and sends the gas refrigerant to the compressor while sending the liquid refrigerant to the evaporator In the refrigerant cycle device that cools the internal atmosphere in the housing by circulating the refrigerant to
The gas-liquid separator delivers the liquid refrigerant in a mode of distributing the liquid refrigerant toward each evaporator.   2. The gas-liquid separator is configured such that liquid refrigerant pipes for sending the liquid refrigerant toward the respective evaporators are respectively inserted into the gas-liquid separator. The refrigerant cycle device according to 1.   The refrigerant inflow portion of each of the liquid refrigerant pipes is installed at a position where the distance from the center of the horizontal cross section of the gas-liquid separator is the same. The refrigerant cycle device described.   4. The refrigerant cycle device according to claim 1, wherein an inner diameter of each of the liquid refrigerant pipes is increased in accordance with a cooling load of a corresponding casing.

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