KR20060089752A - Cooling box - Google Patents

Abstract

In the cooling box of the invention, a box interior cooling heat exchanger is connected to a lower temperature- side heat exchanger mounted in the lower temperature section of a Stirling freeze engine, thereby forming a lower temperature-side refrigerant circulation circuit. The higher temperature section of the Stirling freeze engine has a first higher temperature-side heat exchanger and a second higher temperature-side heat exchanger mounted thereon. The first higher temperature-side heat exchanger has a heat radiation heat exchanger connected thereto, thereby forming a first higher temperature- side refrigerant circulation circuit. The second high temperature-side heat exchanger has connected thereto a heat exchanger for drain evaporation enhancement and a heat exchanger for prevention of dew formation on the cooling box wall, thereby forming a second higher temperature-side refrigerant circulation circuit.

Description

Freezer {COOLING BOX}

The present invention relates to a refrigerator for cooling in a refrigerator by a stirling engine.

The term "freezer" refers to the overall device for lowering the temperature of an enclosed space, called "inside", for the preservation of food and other goods, and includes "freezers", "freezers", "freezers", etc. It does not matter the name as one product.

In the refrigeration cycle of the freezer, a specific proton (CFC: chlorofluorocarbon) or alternative proton (HCFC: hydrochlorofluorocarbon) is used as the refrigerant. Since these refrigerants are released into the atmosphere, the difference in degree leads to the destruction of the ozone layer, and their production and use are subject to international regulations.

Thus, a stirling refrigeration engine that does not use ozone depleting substances as a refrigerant is in the spotlight. In a Stirling refrigeration engine, an inert gas such as helium is used as the working medium, and the piston and the dispenser are operated by external power, and the compression and expansion of the working medium are repeated to form a low temperature part (cold section) and a high temperature part (warm section). . Then, heat is absorbed from the inside in the low temperature part, and heat is radiated from the high temperature part to the surrounding environment. An example of a refrigerator using a Stirling refrigeration engine can be found in Japanese Patent Laid-Open No. 3-36468.

The Stirling refrigeration engine is compact in construction and has a small surface area compared to the refrigeration capacity in both the low temperature portion and the high temperature portion. Therefore, how to perform heat absorption and heat dissipation efficiently has a great influence on the performance of the refrigerator. In the cooling chamber of patent document 1, the heat dissipation fan has a high temperature side heat exchanger of a stirling refrigeration engine in the heat dissipation path which forms an airflow, and is forced to relief heat from a high temperature side heat exchanger by forced air cooling.

In the forced air cooling system configured as described above, a radiator having a large number of fins arranged at a high density must be provided in the high temperature portion in order to extract sufficient heat from the high temperature portion having a small heat transfer area. It is also necessary to flush a large amount of cooling air to the radiator. Such a structure is accompanied with a problem that dust is filled between the heat dissipation fins, the noise caused by the blowing is large, or the blowing fan consumes a large amount of power.

In addition, since the air cooling method has a large heat resistance from the beginning, it is difficult to lose heat. Therefore, there is a problem that the temperature difference between the hot portion and the surrounding environment is not easily reduced, and the COP (coefficient of performance) of the Stirling refrigeration engine is not improved.

In the refrigerator, low temperature air in the furnace contacts the gasket installed in the door or the wall of the refrigerator surrounded by the gasket. As a result, heat is deprived of the outer surface of the gasket or around the cooler wall facing away from the outside, resulting in condensation of moisture in the air. Condensation causes water droplets to fall off and wet the floor, and rust occurs on the walls of the freezer where the steel is painted. In order to prevent this, in a conventional refrigerator, a heat transfer heater is disposed in a wall near the gasket to prevent condensation, and there is a problem that power consumption increases.

In addition, the internal heat exchanger for cooling in the refrigerator inevitably frosts. If the frost is on, the cooling capacity is lowered. Therefore, it is necessary to defrost at that time to restore the cooling capacity. Drain caused by frost melting or other causes is stored in the drain container. In order to eliminate the hassle of removing the drain container one by one and discarding the drain, a technique is generally employed in which heat is applied to the drain container to promote evaporation of the drain. In a conventional refrigerator for compressing a refrigerant by a compressor, the drain container can be heated by using the heat accompanying the refrigerant compression. By the way, the refrigerator using a stirling refrigeration engine does not have the element equivalent to the conventional compressor, and it is necessary to use an electrothermal heater for heating a drain container, and this also became a factor which increases power consumption.

In addition, the electric heat heater is conventionally used also for heating and defrosting the internal heat exchanger for internal cooling, and the electric power consumption has increased by that much.

SUMMARY OF THE INVENTION The present invention has been made in view of the above, and an object thereof is to provide a refrigeration capacity of a stirling refrigeration engine in a refrigerator for performing internal cooling by a stirling refrigeration engine to sufficiently exhibit the freezing ability of the stirling refrigeration engine. There is. Further, the heat generated at the high temperature portion of the stirling refrigeration engine is useful for improving the function of the refrigerator and at the same time reducing the power consumption.

In order to achieve the above object, in the present invention, the refrigerator is configured as follows. That is, in a refrigerator for cooling in a refrigerator by a stirling refrigeration engine, the heat of the high temperature portion of the stirling refrigeration engine is transferred to a gas-liquid two-phase refrigerant, to promote evaporation of the drain, to prevent condensation on the wall of the refrigerator, and to provide a heat exchanger for cooling in the refrigerator. It is used for at least one of defrost.

According to this configuration, the heat of the high temperature portion of the stirling refrigeration engine is transmitted to the refrigerant in the two-liquid gas phase, and is used for at least one of promoting the evaporation of the drain, preventing condensation of the freezer wall, and defrosting of the heat exchanger for the internal cooling. The heat dissipation of the high temperature portion can be effectively used for promoting evaporation of the drain, preventing condensation on the wall of the refrigerator, and defrosting the heat exchanger for cooling in the refrigerator. As a result, the maintenance maintenance of the drain can be reduced. In addition, it is possible to perform defrosting of the internal heat exchanger by preventing condensation on the wall of the refrigerator without using a heat transfer heater, thereby improving the function or usability of the refrigerator, and consuming more heat than using the heat transfer heater. Power can be suppressed.

In addition, since the heat from the drain water, the condensation alarm unit, or the internal cooling refrigeration heat exchanger is recovered, the cold heat having a lower temperature than the surrounding environment is recovered and the high temperature part of the stirling refrigeration engine is cooled, thereby improving the heat radiation efficiency of the entire heat dissipation system. The COP of a stirling refrigeration engine can also be improved and the power consumption of a refrigerator can be reduced.

In addition, since the refrigerant is used in the gas-liquid two-phase type, latent heat of evaporation and condensation of the refrigerant is used for heat exchange, whereby the thermal resistance can be suppressed to be small, and the heat dissipation efficiency is increased. As a result, the heat exchange efficiency is dramatically increased, the efficiency of the Stirling refrigeration engine can be improved, and power consumption can be reduced.

Moreover, in this invention, a refrigerator is comprised as follows. That is, in the refrigerator which performs in-vehicle cooling by the Stirling refrigeration engine, the 1st high temperature side refrigerant circulation circuit which heat-dissipates the heat of the high temperature part of the said stirling refrigeration engine outside, and the heat | fever of the said high temperature part promotes evaporation of a drain, and a cooler A second high temperature side refrigerant circulation circuit is used for at least one of the defrost of the wall and the defrost of the heat exchanger for cooling in the refrigerator.

According to this structure, the heat of a high temperature part can be stably radiated by providing the 1st high temperature side refrigerant | circulation refrigerant | circuit circuit which heats the heat of the high temperature part of a stirling refrigeration engine outside. In addition, since a second high temperature side refrigerant circulation circuit is used in which the heat of the high temperature portion is used for at least one of promoting the evaporation of the drain, preventing condensation of the freezer wall, and defrost of the internal heat exchanger for cooling, the heat dissipation of the high temperature portion of the stirling refrigeration engine is drained. It can be effectively used for the promotion of evaporation, prevention of condensation on the wall of the refrigerator, and defrosting of the heat exchanger for cooling in the refrigerator. As a result, the maintenance maintenance of the drain can be reduced. In addition, it is possible to perform defrosting of the internal heat exchanger by preventing condensation on the wall of the refrigerator without using a heat transfer heater, thereby improving the function or usability of the refrigerator, and at the same time, power consumption compared to when heating is performed by the heat transfer heater. Can be suppressed.

In addition, since the heat from the drain water, the condensation alarm unit, or the internal cooling refrigeration heat exchanger is recovered, the cold heat having a lower temperature than the surrounding environment is recovered and the high temperature part of the stirling refrigeration engine is cooled, thereby improving the heat radiation efficiency of the entire heat dissipation system. The COP of a stirling refrigeration engine can also be improved and the power consumption of a refrigerator can be reduced.

In the present invention, in the refrigerator configured as described above, the first high temperature side refrigerant circulation circuit and the second high temperature side refrigerant circulation circuit are independent of each other.

According to this configuration, since the first high temperature side refrigerant circulation circuit and the second high temperature side refrigerant circulation circuit are independent of each other, the second high temperature side refrigerant circulation circuit is movably activated while ensuring heat dissipation by the first high temperature side refrigerant circulation circuit. It can be utilized to promote the evaporation of the drain, to prevent condensation on the wall of the refrigerator, or to defrost the heat exchanger for cooling in the refrigerator as needed. This means that the circulation pump in the second high-temperature-side refrigerant circulation circuit is not always operated, but only when it is necessary to promote the evaporation of the drain and to prevent condensation around the door. Thereby, the power consumption of a circulation pump can be saved and the operation life of a circulation pump can be extended. In addition, since the periphery of the door is not heated longer than necessary, the heat load of the refrigerator can be reduced to suppress power consumption.

In the present invention, in the refrigerator configured as described above, the refrigerant is circulated by natural circulation in the first high temperature side refrigerant circulation circuit, and the refrigerant is circulated by forced circulation in the second high temperature side refrigerant circulation circuit. .

According to this configuration, since the refrigerant is circulated by natural circulation in the first high temperature side refrigerant circulation circuit, and the refrigerant is circulated by forced circulation in the second high temperature side refrigerant circulation circuit, the artificial body is artificial in the first high temperature side refrigerant circulation circuit. Constant heat dissipation can be achieved without using energy. In the other 2nd high temperature side refrigerant | circulation refrigerant | circuit circuit, it is possible to force | circulate a refrigerant | coolant dynamically by the time required, and to recover heat radiation or cold heat. Thereby, cooling can be performed efficiently, without unnecessary energy consumption.

Moreover, in this invention, a refrigerator is comprised as follows. That is, in the refrigerator which performs in-vehicle cooling by a Stirling refrigeration engine, the high temperature side heat exchanger installed in the high temperature part of the Stirling refrigeration engine, the heat exchanger for heat dissipation to a high-temperature environment, and the said high temperature side heat exchanger and heat dissipation A first high temperature side refrigerant circulation circuit, which is a loop thermosiphon formed between the heat exchangers, and the heat of the high temperature portion for at least one of promoting the evaporation of the drain, preventing condensation of the cooler wall, and defrost of the internal heat exchanger. And a high temperature side refrigerant circulation circuit and a circulation pump for delivering the refrigerant in the high temperature side heat exchanger to the second high temperature side refrigerant circulation circuit.

According to this structure, since the 1st high temperature side refrigerant circulation circuit which is a loop type thermo siphon is formed between the high temperature side heat exchanger installed in the high temperature part of a stirling refrigeration engine, and the heat exchanger for heat dissipation to an outside environment, it is high temperature The first high temperature side refrigerant circulation circuit can be released from the side heat exchanger without using artificial energy. In the second second high-temperature refrigerant circulation circuit, the refrigerant is transferred by a circulation pump so that the heat of the high-temperature portion can be reliably used for at least one of promotion of evaporation of the drain, prevention of condensation on the cooler wall, and defrost of the internal heat exchanger for cooling in the refrigerator. have.

Moreover, in this invention, a refrigerator is comprised as follows. That is, in the refrigerator which performs in-vehicle cooling by the Stirling refrigeration engine, the 1st high temperature side refrigerant circulation circuit which heat-dissipates the heat of the high temperature part of the said stirling refrigeration engine outside, and the heat | fever of the said high temperature part promotes evaporation of a drain, and a cooler A second high temperature side refrigerant circulation circuit and a second high temperature side refrigerant circulation circuit are provided in the high temperature section while forming a second high temperature side refrigerant circulation circuit used for at least one of a defrost of a wall and preventing defrost of the internal heat exchanger. The common high temperature side heat exchangers are connected in parallel with each other.

According to this configuration, the first high temperature side refrigerant circulation circuit for dissipating the heat of the hot portion of the stirling refrigeration engine to the outside, and during the defrost of the heat exchanger for promoting the evaporation of the drain, preventing condensation of the cooler wall, and cooling in the cold compartment The first high temperature side refrigerant circulation circuit to be used for at least one is formed, and the first high temperature side refrigerant circulation circuit and the second high temperature side refrigerant circulation circuit are connected in parallel to a common high temperature side heat exchanger provided in the high temperature portion in parallel with each other. Even if the circuit becomes unusable by either cause in one of the high temperature side refrigerant circulation circuit and the second high temperature side refrigerant circulation circuit, the heat radiation from the high temperature portion can be continued by the other circuit. As a result, it is easy to avoid a situation in which the Stirling refrigeration engine is poor in heat radiation and damaged.

In the present invention, in the refrigerator configured as described above, a plurality of the high temperature side heat exchangers are provided, and a first high temperature side refrigerant circulation circuit and a second high temperature side refrigerant circulation circuit are respectively provided in the plurality of high temperature side heat exchangers. Are connected in parallel to each other.

Then, the refrigerant is supplied from the entirety of the plurality of high temperature side heat exchangers to the first high temperature side refrigerant circulation circuit and the second high temperature side refrigerant circulation circuit, and the first high temperature side refrigerant is supplied to all of the plurality of high temperature side heat exchangers. The refrigerant is refluxed from the circulation circuit and the second high temperature side refrigerant circulation circuit.

In addition, the first high temperature side refrigerant circulation circuit is configured as a loop type thermosiphon, and the second high temperature side refrigerant circulation circuit is provided with a circulation pump for delivering the refrigerant in the high temperature side heat exchanger to the second high temperature side refrigerant circulation circuit. do.

The circulation pump is also disposed at the most upstream portion of the second high temperature side refrigerant circulation circuit.

According to this configuration, since a plurality of high temperature side heat exchangers are provided and the first high temperature side refrigerant circulation circuit and the second high temperature side refrigerant circulation circuit are connected to each other in parallel to each of the plurality of high temperature side heat exchangers, any high temperature side Even if the heat exchanger is removed, a plurality of high temperature side refrigerant circulation circuits are secured, and it is easy to avoid a situation such as stopping of the refrigerant circulation due to the blockage of the circuit.

Then, the refrigerant is supplied to the first high temperature side refrigerant circulation circuit and the second high temperature side refrigerant circulation circuit from all of the plurality of high temperature side heat exchangers, and the first high temperature side refrigerant circulation circuit is supplied to all of the plurality of high temperature side heat exchangers. Since the refrigerant is refluxed from the second high temperature side refrigerant circulation circuit, all of the plurality of high temperature side heat exchangers can be involved in the heat supply to the outside.

Further, since the first high temperature side refrigerant circulation circuit is configured as a loop type thermosiphon, heat can be released from the high temperature side heat exchanger without using artificial energy by using the first high temperature side refrigerant circulation circuit. In the second high temperature side refrigerant circulation circuit, the refrigerant is transferred by a circulation pump so that the heat of the high temperature portion can be reliably used for at least one of promoting the evaporation of the drain, preventing condensation on the cooler wall, and defrost of the internal heat exchanger for cooling in the interior. .

In addition, since the circulation pump is disposed at the uppermost part of the second high temperature side refrigerant circulation circuit, the resistance of the pipeline from the high temperature side heat exchanger to the circulation pump is small, and the refrigerant flows smoothly into the circulation pump. If the resistance of the conduit for supplying the refrigerant to the circulation pump is large, a cavity phenomenon may occur on the suction side of the circulation pump, and the refrigerant may evaporate unnecessarily, thereby impairing the circulation efficiency. Such a situation can be avoided by placing the circulation pump at the uppermost part of the second high temperature side refrigerant circulation circuit.

In the present invention, in the refrigerator constituted as described above, the reflux refrigerant pipe of the first high temperature side refrigerant circulation circuit is connected to the suction side of the circulation pump.

According to this structure, since the reflux refrigerant pipe of the first high temperature side refrigerant circulation circuit is connected to the suction side of the circulation pump, the saturation temperature at which the first high temperature side refrigerant circulation circuit flows to the refrigerant flowing through the second high temperature side refrigerant circulation circuit. Can be combined to increase the total amount of heat of the refrigerant flowing in the second high temperature side refrigerant circulation circuit. Thereby, the utilization efficiency of the heat which generate | occur | produces a stirling refrigeration engine can be improved.

In the present invention, in the refrigerator configured as described above, the refrigerant is used as a gas-liquid two-phase type in one or both of the first high temperature side refrigerant circulation circuit and the second high temperature side refrigerant circulation circuit.

According to this configuration, in one or both of the first high temperature side refrigerant circulation circuit and the second high temperature side refrigerant circulation circuit, since the refrigerant is used in the gas-liquid two-phase type, latent heat of evaporation and condensation of the refrigerant is used for heat exchange. The resistance can be suppressed small, and the heat radiation efficiency is increased. As a result, the heat exchange efficiency is dramatically increased, the efficiency of the Stirling refrigeration engine can be improved, and power consumption can be reduced.

Moreover, in this invention, a refrigerator is comprised as follows. That is, in the refrigerator which performs internal cooling by the Stirling refrigeration engine, the heat exchange part provided in order to promote the evaporation of a drain, and the heat exchange part provided in order to prevent dew condensation of a cooler wall are connected in parallel, and this parallel connection structure is mentioned above. A high temperature side refrigerant circulation circuit is formed in series with a heat exchanger installed in the high temperature section of the stirling refrigeration engine.

According to this structure, the heat exchange part provided in order to promote the evaporation of a drain, and the heat exchange part provided in order to prevent condensation of a freezer wall are connected in parallel, and this parallel connection structure is connected in series with the heat exchanger provided in the high temperature part of a stirling refrigeration engine. Therefore, since the high temperature side refrigerant circulation circuit is formed, the heat dissipation of the high temperature portion of the Stirling refrigeration engine can be effectively utilized for promoting the evaporation of the drain and preventing condensation on the freezer wall. As a result, the maintenance maintenance of the drain can be reduced. In addition, condensation on the cooler wall can be prevented without using a heat transfer heater, and the function or usability of the cooler can be improved, and power consumption can be reduced as compared with the case where a heat transfer heater is used.

In addition, since latent heat of evaporation and condensation of the refrigerant is used for heat exchange, heat resistance can be reduced to a small degree, and heat dissipation efficiency is increased. Thereby, the efficiency of a stirling refrigeration engine can be improved and power consumption can be reduced.

In addition, since the cold water having a lower temperature than the surrounding environment is recovered from the drain water and the condensation alarm unit to cool the hot portion of the Stirling refrigeration engine, the heat radiation efficiency of the entire heat dissipation system is improved. The COP of a stirling refrigeration engine can also be improved and the power consumption of a refrigerator can be reduced.

In addition, since the heat exchange part installed to promote evaporation of the drain and the heat exchange part installed to prevent condensation of the freezer wall are connected in parallel, the flow resistance of the refrigerant can be lowered. Since the flow resistance of the refrigerant is low, when the circulation pump is used, the power consumption can be significantly reduced.

In the parallel structure, when the valves are connected in series to the heat exchanger provided for promoting evaporation of the drain and the heat exchanger provided for preventing condensation of the cooler wall, the refrigerant needs to flow at that point. The heat exchange part on the side without can stop the flow of refrigerant, and can reduce its power consumption by reducing the load of the circulation pump. In addition, since the periphery of the door is not heated longer than necessary, the heat load of the refrigerator can be reduced to suppress power consumption.

Moreover, in this invention, a refrigerator is comprised as follows. That is, in a refrigerator for performing in-vehicle cooling by a stirling refrigeration engine, a heat exchanger installed at a high temperature portion of the stirling refrigeration engine, a heat exchanger provided for promoting evaporation of a drain, and a condenser to prevent condensation on the wall of the freezer. The heat exchange unit is connected in series to form a high temperature side refrigerant circulation circuit.

According to this configuration, a high temperature side refrigerant circulation circuit is formed by connecting a heat exchanger installed at a high temperature portion of the stirling refrigeration engine, a heat exchanger installed to promote evaporation of the drain, and a heat exchanger installed to prevent condensation on the cooler wall. Therefore, the heat dissipation of the high temperature portion of the stirling refrigeration engine can be effectively utilized for promoting the evaporation of the drain and preventing the condensation of the freezer wall. As a result, the maintenance maintenance of the drain can be reduced. In addition, condensation on the cooler wall can be prevented without using a heat transfer heater, and the function or usability of the cooler can be improved, and power consumption can be reduced as compared with the case where a heat transfer heater is used.

In addition, since the heat exchanger installed in the high temperature part of the stirling refrigeration engine, the heat exchanger installed to promote evaporation of the drain, and the heat exchanger installed to prevent condensation of the freezer wall are connected in series, the piping configuration is simple and the number of assembly processes is small. Lose.

In the present invention, in the refrigerator configured as described above, a low temperature side refrigerant circulation circuit including a heat exchanger installed at a low temperature portion of the Stirling refrigeration engine and an internal cooling heat exchanger is provided, and A defrost heat exchanger is provided, and a high temperature side refrigerant circulation circuit including the defrost heat exchanger and a heat exchanger provided at a high temperature portion of the stirling refrigeration engine is formed.

According to this configuration, a low temperature refrigerant circulation circuit including a heat exchanger installed at a low temperature portion of the stirling refrigeration engine and a heat exchanger for internal cooling is formed, and a defrost heat exchanger is provided for the internal cooling heat exchanger. And a high temperature side refrigerant circulation circuit including a heat exchanger installed in the high temperature portion of the stirling refrigeration engine, the frost can be removed without using the defrosting heat transfer heater. Since the cold heat of frost is recovered and the high temperature part is cooled, the heat load of the heat dissipation system is reduced, and the heat dissipation efficiency of the whole heat dissipation system is also improved.

In the present invention, in the refrigerator configured as described above, a heat storage unit is provided in a high temperature side refrigerant circulation circuit including a heat exchanger installed in the defrost heat exchange unit and a high temperature unit of the Stirling refrigeration engine.

According to this configuration, since the heat storage unit is installed in the high temperature side refrigerant circulation circuit including the defrost heat exchange unit and the heat exchanger installed in the high temperature unit of the stirling refrigeration engine, the frost is removed by using the heat accumulated in the heat storage unit even when the stirling refrigeration engine is stopped. Can be done. Since the cold heat of frost is collected in the heat storage portion and used to cool the high temperature portion during normal operation, the heat load of the heat dissipation system is reduced, and the heat dissipation efficiency of the entire heat dissipation system is also improved. As a result, the operating COP of the stirling refrigeration engine 30 is improved, and power consumption can be reduced.

1 is a cross-sectional view of a refrigerator.

2 is a piping configuration diagram showing the first embodiment of the refrigerator according to the present invention.

3 is a piping configuration diagram showing a second embodiment of the refrigerator according to the present invention.

4 is a piping configuration diagram showing a third embodiment of the refrigerator according to the present invention.

5 is a piping configuration diagram showing a fourth embodiment of the refrigerator according to the present invention.

6 is a piping configuration diagram showing the fifth embodiment of the refrigerator according to the present invention.

7 is a piping configuration diagram showing a sixth embodiment of the refrigerator according to the present invention.

8 is a piping configuration diagram showing the seventh embodiment of the refrigerator according to the present invention.

9 is a piping configuration diagram showing an eighth embodiment of a refrigerator according to the present invention.

10 is a piping configuration diagram showing the ninth embodiment of the refrigerator according to the present invention.

11 is a piping configuration diagram showing a tenth embodiment of the refrigerator according to the present invention.

12 is a piping configuration diagram showing an eleventh embodiment of the refrigerator according to the present invention.

Fig. 13 is a piping configuration diagram showing a twelfth embodiment of the refrigerator according to the present invention.

14 is a piping configuration diagram showing a thirteenth embodiment of a refrigerator according to the present invention.

Fig. 15 is a piping configuration diagram showing a fourteenth embodiment of the refrigerator of the present invention.

Fig. 16 is a piping configuration diagram showing a fifteenth embodiment of a refrigerator according to the present invention.

Fig. 17 is a piping configuration diagram showing a sixteenth embodiment of the refrigerator according to the present invention.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described based on drawing.

1 shows a cross section of a refrigerator. The refrigerator 1 is for food preservation, and is provided with the housing 10 of a heat insulation structure. The housing 10 is provided with three upper and lower cooling chambers 11, 12, 13. The cooling chambers 11, 12, 13 have openings in the front side (left side in FIG. 1) of the housing 10, respectively, and the heat insulation doors 14, 15, 16 which can open and close this opening are closed. Gaskets 17 of a type surrounding the openings of the cooling chambers 11, 12, 13 are mounted on the back sides of the heat insulating doors 14, 15, 16. Inside the cooling chambers 11, 12, 13, the shelf 18 suitable for the kind of food to be accommodated is provided suitably.

A cooling system and a heat dissipation system centered on the Stirling refrigeration engine are provided from the top surface to the rear surface or the bottom surface of the housing 10. 1 (sectional drawing) and FIG. 2 (piping configuration diagram) are 1st Embodiment.

The storage space 19 is provided in each of the upper surface and the rear surface of the housing 10, and the Stirling refrigeration engine 30 is provided here. A part of the Stirling refrigeration engine 30 becomes a low temperature part, and the low temperature side heat exchanger 41 is provided here. In the cooling chamber 13, a heat exchanger 42 for internal cooling is installed. The low temperature side heat exchanger 41 and the internal cooling heat exchanger 42 are connected by a refrigerant pipe to form a low temperature side refrigerant circulation circuit 40 (see Fig. 2). The low temperature side refrigerant circulation circuit 40 is filled with natural refrigerant such as CO ₂ . A large number of fins are provided inside the low temperature side heat exchanger 41 so that heat can be efficiently exchanged with the refrigerant.

Inside the housing 10, a duct 20 is provided for distributing air deprived of heat by the internal heat exchanger 42 for cooling to the cooling chambers 11, 12, 13. The duct 20 has a cold air outlet 21 communicating with the cooling chambers 11, 12, 13 in place. The blowing fan 22 for forcibly sending cold air is provided in place inside the duct 20.

Although not shown, the duct which collect | recovers air from the cooling chambers 11, 12, 13 is also provided in the housing | casing 10. As shown in FIG. This duct has a blowout port below the in-cooling heat exchanger 42, and supplies air to be cooled to the in-cooling heat exchanger 42 as shown by the broken arrow in FIG.

The drain accommodating trough 25 is provided below the in-vehicle heat exchanger 42. The drain accommodating trough 25 collects the drain falling from the internal heat exchanger 42 for cooling and flows it to the drain container 26 provided in the bottom surface of the housing 10.

The other part of the Stirling refrigeration engine 30 becomes a high temperature part, and a high temperature side heat exchanger is installed here. In the case of 1st Embodiment, the high temperature side heat exchanger consists of the 1st high temperature side heat exchanger 51 and the 2nd high temperature side heat exchanger 61 of the shape which cut the ring in half. A plurality of fins are provided in each of the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61, so that heat can be efficiently exchanged with the refrigerant.

If the high temperature side heat exchanger is in the form of a single ring, it is necessary to strictly manage and fit the shape to ensure accuracy in order to firmly contact the high temperature portion of the stirling refrigeration engine 30. However, in the present embodiment, since the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61 have a shape in which the ring is cut in half, the high temperature portion of the stirling refrigeration engine 30 is sandwiched and fastened therebetween. By adjusting the tightening pressure at the time of attachment, the contact pressure with a high temperature part can be controlled. In other words, the contact pressure is insufficient due to the shape error, and the heat transfer rate between the high temperature portion and the like decreases. Splitting the ring into more blocks can be said to be the same.

The first high temperature side refrigerant circulation circuit 50 is configured to include the first high temperature side heat exchanger 51, and the second high temperature side refrigerant circulation circuit is configured to include the second high temperature side heat exchanger 61 ( 60).

The first high temperature side refrigerant circulation circuit 50 includes a first high temperature side heat exchanger 51, a heat dissipation heat exchanger 52 provided on an upper surface of the housing 10, and a refrigerant pipe connecting them in a closed loop. It is composed. The heat exchanger 52 for heat dissipation heat-dissipates in an external environment, and the blower fan 53 is provided. The first high temperature side refrigerant circulation circuit 50 seals water (including an aqueous solution) or hydrocarbon refrigerant. The first high temperature side refrigerant circulation circuit 50 functions as a loop thermosiphon so that the refrigerant is naturally circulated.

The second high temperature side refrigerant circulation circuit 60 is formed by the second high temperature side heat exchanger 61, the heat exchangers 62 and 63, the refrigerant forced circulation pump 64, and a refrigerant pipe connecting them. It is made. In the second high temperature side refrigerant circulation circuit 60, natural refrigerant such as water is enclosed. In addition, in this specification, the refrigerant | coolant discharge side of the 2nd high temperature side heat exchanger 61 is represented by the "upstream part" of the 2nd high temperature side refrigerant circuit 60. As shown in FIG. The circulation pump 64 is arrange | positioned at this uppermost part.

The heat exchange part 62 is a zigzag of a part of the pipe, and is disposed under the drain container 24 to serve to promote the evaporation by heating the drain accumulated in the drain container 24 by the heat of the refrigerant. do.

The heat exchange part 63 arrange | positions a part of piping to the opening part of the cooling chambers 11, 12, 13, and plays a role which prevents dew condensation by heating this part by the heat which a refrigerant has.

Subsequently, the operation of the refrigerator 1 will be described.

When the stirling refrigeration engine 30 is driven, the low temperature part cools, and the high temperature part rises in temperature. The low temperature side heat exchanger (41) loses heat, and the refrigerant inside flows into the internal heat exchanger (42) for cooling inside the low temperature refrigerant circulation circuit (40) in a condensed state.

The refrigerant flowing into the in-vehicle heat exchanger 42 evaporates in the in-vehicle heat exchanger 42 to lower the surface temperature of the in-vehicle heat exchanger 42. The air exiting the internal cooling heat exchanger (42) is deprived of heat and becomes cold air, and is taken out from the cold air outlet 21 of the duct 20 to the cooling chambers 11, 12, 13, and the cooling chambers 11, 12, Lower the temperature of 13). Thereafter, the air is returned to the in-vehicle cooling heat exchanger 42 through a duct not shown.

The evaporated refrigerant is refluxed to the low temperature side heat exchanger (41) through the low temperature side refrigerant circulation circuit (40), deprives heat, and condenses it. And it flows again to the internal heat exchanger 42 for cooling.

Heat generated by the Stirling refrigeration engine 30 to work, and heat recovered from the inside of the low temperature portion is radiated from the high temperature portion. By this heat, the 1st high temperature side heat exchanger 51 and the 2nd high temperature side heat exchanger 61 are heated.

When the first high temperature side heat exchanger 51 is heated, the internal refrigerant evaporates and flows into the heat radiating heat exchanger 52. The blower fan 53 blows out air on the surface of the heat exchanger 52 for heat dissipation, and the refrigerant takes heat away and condenses it. The condensed refrigerant is refluxed to the first high temperature side heat exchanger 51 and evaporated again. In this way, a cycle is repeated in which the refrigerant receives heat from the high temperature portion of the stirling refrigeration engine 30 and evaporates, and condenses it by transferring it to the cooling air in the heat radiation heat exchanger 52.

In the first high temperature side refrigerant circulation circuit 50, the refrigerant is used as a gas-liquid two-phase type in which a gaseous phase and a liquid phase are mixed. In the heat exchange involving the phase change of the gas-liquid two-phase, the refrigerant is evaporated / condensed to perform latent heat. As a result, the heat transfer rate is remarkably improved as compared with the heat exchange without a phase change.

The above is explained. The heat radiation amount Q of the Stirling refrigeration engine 30 is represented by the following formula.

Q = h · A · ΔTm

here,

h: heat transfer rate

A: heat transfer area

ΔTm: temperature difference

Therefore, the higher the heat transfer rate h, the lower the hot part temperature of the Stirling refrigeration engine 30, and the COP can be improved.

In general, in the use of a blind refrigerant that does not involve a phase change, the heat transfer rate is several hundred to 1000 w / m 2k. In addition, the heat transfer rate is proportional to the power consumption of the pump to circulate the blind.

On the other hand, in the heat exchange accompanied by the phase change of the gas-liquid two-phase, since the latent heat of the evaporation / condensation process of the refrigerant is used, a heat transfer rate of 3000 to 10000 w / m 2k can be obtained. The value of this heat transfer rate reaches several to several tens of times in the case of a blind system.

In the first high temperature side refrigerant circulation circuit 50, since the refrigerant is circulated as the gas-liquid two-phase as described above, heat can be efficiently exchanged. The heat resistance generated at the time of heat exchange is very low, and the hot part of the stirling refrigeration engine 30 is kept at a lower temperature even under the same conditions (equal environment temperature, equivalent heat dissipation amount). As a result, the operating COP of the stirling refrigeration engine 30 is improved, and power consumption can be reduced.

When the second high temperature side heat exchanger 61 is heated, the refrigerant evaporates. Here again, the refrigerant is used as a gas-liquid two-phase type. The circulating pump 64 delivers the refrigerant of the gas-liquid two-phase to the heat exchange parts 62 and 63.

The coolant first flows through the heat exchanger 62, and heats the drain vessel 26 thereon. As a result, the drain in the drain container 26 rises in temperature without using an electric heater, and evaporation is promoted. Therefore, the operation | movement which discards the drain accumulated in the drain container 26 is unnecessary, and the maintenance maintenance of a drain can be aimed at.

Subsequently, the refrigerant flows through the heat exchange part 63, and heats around the openings of the cooling chambers 11, 12, 13. Condensation is likely to occur in a portion near the gasket 17 in contact with the housing 10, that is, in the boundary between the inside and the outside of the gasket, but the temperature of the portion in contact with the outside air of the cooler wall by passing the coolant above the dew point temperature is higher than the dew point temperature. And condensation is prevented without using an electrothermal heater.

The coolant recovers cold heat from the drain in the heat exchange part 62, and recovers cold heat from the housing 10 in the heat exchange part 63. Thus, the refrigerant | coolant which collect | recovered cold heat returns to the liquid phase, and flows into the 2nd high temperature side heat exchanger 61 of a liquid phase form. In contact with the gaseous phase, the gaseous phase is liquefied to lower the vapor pressure, thereby promoting evaporation and recovering the gas-liquid two-phase again. In this way, a cycle in which the refrigerant receives heat from the high temperature portion of the Stirling refrigeration engine 30 and evaporates, condenses and radiates heat in the heat exchangers 62 and 63 to recover the cold heat is repeated. When the circulation pump 64 stops running, this cycle is stopped.

The coolant supplies warm heat to the drain and near the openings of the cooling chambers 11, 12, 13, and instead recovers cold heat at a lower temperature than the environment to cool the hot portion of the stirling refrigeration engine 30. This reduces the heat load of the heat dissipation system and improves the heat dissipation efficiency of the entire heat dissipation system. As a result, the operating COP of the stirling refrigeration engine 30 is improved, and power consumption can be reduced.

The first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60 are independent of each other and are provided in parallel. For this reason, the heat dissipation by the 1st high temperature side refrigerant | coolant circulation circuit 50 and the heat dissipation by the 2nd high temperature side refrigerant | coolant circulation circuit 60 can be performed independently without mutual dependence. This means that individual operation control is possible based on the heat load state of the refrigerator 1. For example, the circulation pump 64 is not always operated, but can be operated only when it is necessary to promote drain evaporation or to prevent condensation around the door. Thereby, the power consumption of the circulation pump 64 can be saved, and the operating life of the circulation pump 64 can be extended.

In addition, since the circulation pump 64 is disposed at the most upstream portion of the second high temperature side refrigerant circulation circuit 60, there is little pipeline resistance from the second high temperature side heat exchanger 61 to the circulation pump 64, and the refrigerant is smooth. Flows into the circulation pump (64). If the resistance of the pipe for supplying the refrigerant to the circulation pump 64 is large, a cavity phenomenon occurs on the suction side of the circulation pump 64, and the refrigerant may evaporate unnecessarily, thereby impairing the circulation efficiency. Is disposed at the most upstream portion of the second high temperature side refrigerant circulation circuit 60, such a situation can be avoided.

As to the two-phase gas-liquid phase, in the second high temperature side refrigerant circulation circuit 60, the refrigerant may be only a liquid phase in the vicinity of where the heat treatment parts 62 and 63 perform drain treatment and condensation prevention. When the refrigerant is refluxed to the second high temperature side heat exchanger 61, latent heat exchange between the liquid and the refrigerant vapor is possible, whereby a high heat exchange efficiency can be obtained.

Next, 2nd Embodiment The following embodiment is described based on the drawing of FIG. 3 to 17 are all piping configuration diagrams, and it is assumed that the piping shown therein is realized in the refrigerator 1 of FIG. About the component which is common in 1st Embodiment, the code | symbol used by description of 1st Embodiment is used as it is, and description is abbreviate | omitted.

3 shows a second embodiment of the refrigerator of the present invention. Here, the heat exchanger 62 for promoting evaporation of the drain and the heat exchanger 63 for preventing condensation of the freezer wall are connected in parallel, and the parallel connection structure is connected to the second high temperature side heat exchanger 61 and the circulation pump 64. Connect in series. The circulation pump 64 is also disposed at the most upstream portion of the second high temperature side refrigerant circulation circuit 60 here. In the parallel connection structure, the valve 65 is connected in series to the upstream side of the heat exchange part 62, and the valve 66 is connected in series to the upstream side of the heat exchange part 63.

According to the said structure, the flow resistance of the refrigerant | coolant in the site | part of the heat exchange part 62, 63 becomes about half of 1st Embodiment, and can reduce the power consumption of the circulation pump 64 significantly. In addition, since the valves 65 and 66 are combined with the heat exchangers 62 and 63, if any one of the promotion of the evaporation of the drain and the prevention of condensation of the freezer wall is not necessary, the valve on the side that is not required is closed to flow the refrigerant. Can stop. By reducing the load of the circulation pump, the power consumption of the circulation pump 64 can be further reduced.

If the valve 66 is closed except when necessary to prevent condensation, the periphery of the doors 14, 15, and 16 will not be heated longer than necessary. Thereby, the heat load of the cooling chambers 11, 12, 13 can be reduced, and power consumption can be suppressed.

Instead of providing a dedicated valve in each of the heat exchange parts 62 and 63, a common three-way valve is provided, and by switching operation of the three-way valve, a refrigerant | coolant is added to both of the heat exchange parts 62 and 63. 3 states of "pass through", "coolant passes only through heat exchanger 62", and "coolant passes only through heat exchanger 63". In addition, in order to facilitate automatic control, it is recommended that the valve be a solenoid valve.

The refrigerant flowing through the first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60 are both gas-liquid two phases.

3 shows a third embodiment of the refrigerator of the present invention. In an environment with high humidity, it is necessary to constantly promote the evaporation of the drain and to prevent the condensation of the freezer wall, but the piping structure of the third embodiment is suitable for such a case.

In the third embodiment, a single high temperature side heat exchanger 71 is provided at a high temperature portion of the stirling refrigeration engine 30. Like the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61, a plurality of fins are provided inside the high temperature side heat exchanger 71 so that heat exchange can be efficiently performed with the refrigerant. It is. The high temperature side heat exchanger 71 has a circulation pump 64, a heat exchange part 62 for promoting evaporation of a drain, a heat exchanger 63 for preventing condensation of a cooler wall, and a heat exchanger for radiating heat from the upstream side of the refrigerant flow. 52 are connected to form a series circuit, and constitute the high temperature side refrigerant circulation circuit 70.

When the stirling refrigeration engine 30 is driven, the high temperature side heat exchanger 71 is heated. When the high temperature side heat exchanger 71 is heated, the refrigerant evaporates to form a gas-liquid two-phase type in which a gas phase and a liquid phase are mixed. By the circulation pump 64 disposed at the most upstream portion of the high temperature side refrigerant circulation circuit 70, the refrigerant in the gas-liquid two-phase is sent to the heat exchange part 62.

The refrigerant in the gas-liquid two-phase flows through the heat exchange part 62 and transfers heat to the drain container 26 to promote evaporation of the drain. The coolant continuously flows through the heat exchanger 63, and transfers heat to a portion in contact with the outside air of the cooler wall to maintain the temperature of the portion above the dew point temperature.

The coolant recovered from the drain in the heat exchanger 62 and the coolant recovered from the housing 10 in the heat exchanger 63 flows into the heat exchanger 52 for heat dissipation in a state in which the gaseous phase is returned to the liquid phase. . Since the blower fan 53 discharges air to the surface of the heat exchanger 52 for heat dissipation, the refrigerant is further deprived of heat to liquefy and proceeds to the high temperature side heat exchanger 71 in the form of an almost liquid phase. Then, some evaporate and recover the gas-liquid phase 2 again. In this way, a cycle in which the refrigerant receives heat from the high temperature portion of the Stirling refrigeration engine 30 and evaporates, condenses and radiates heat in the heat exchangers 62 and 63 to recover the cold heat is repeated. When the circulation pump 64 stops running, this cycle is stopped.

According to the above configuration, there is an advantage that the piping structure of the high temperature side refrigerant circulation circuit 70 is simple and the number of assembling steps is reduced.

The positions of the heat exchangers 62 and 63 may be reversed to first heat the cooler wall and then to heat the drain container 26. Moreover, although heat conveyance by the refrigerant | coolant of two gas-liquid phases is preferable, the heat conveyance by the liquid-based blind system is also employable.

5 shows a fourth embodiment of the refrigerator of the present invention. Also in 4th Embodiment, the single type high temperature side heat exchanger 71 is provided in the high temperature part of the Stirling refrigeration engine 30. As shown in FIG. A large number of fins are provided inside the high temperature side heat exchanger 71 so that heat can be efficiently exchanged with the refrigerant. The circulation pump 64 is connected to the downstream side of the high temperature side heat exchanger 71, and the heat exchanger 52 for heat radiation is connected to the upstream side.

Between the circulation pump 64 and the heat dissipation heat exchanger 52, a heat exchange part 62 for promoting evaporation of the drain and a heat exchanger 63 for preventing condensation of the freezer wall are disposed. The heat exchange parts 62 and 63 are not connected in series as in the third embodiment but in parallel as in the second embodiment. This parallel connection structure is connected in series with the high temperature side heat exchanger 71 and the circulation pump 64. In the parallel connection structure, the valve 65 is connected in series to the upstream side of the heat exchange part 62, and the valve 66 is connected in series to the upstream side of the heat exchange part 63. In this way, the high temperature side refrigerant circulation circuit 70 is configured.

When the stirling refrigeration engine 30 is driven, the high temperature side heat exchanger 71 is heated. When the high temperature side heat exchanger 71 is heated, a part of the refrigerant inside evaporates and the refrigerant becomes a gas-liquid two-phase type. The refrigerant in the two gas-liquid phases is sent to the heat exchange parts 62 and 63 by the circulation pump 64 disposed at the uppermost part of the high temperature side refrigerant circulation circuit 70.

The refrigerant is separated and flows through the heat exchange parts 62 and 63, heat is transferred to the drain vessel 26 to promote evaporation of the drain, and heat is transferred to a part of the cooler wall in contact with the outside air, thereby converting the temperature of this part to the dew point temperature. Keep above.

The coolant that recovers the cold heat from the drain in the heat exchanger 62 and the coolant recovered from the housing 10 in the heat exchanger 63 flows into the heat exchanger 52 for heat dissipation in a state where the gaseous phase is returned to the liquid phase. . Since the blower fan 53 blows out the air on the surface of the heat exchanger 52 for heat dissipation, the refrigerant is further deprived of heat to liquefy and proceeds to the high temperature side heat exchanger 71 in a nearly liquid single phase form. Then, some evaporate and recover the gas-liquid phase 2 again. In this way, a cycle in which the refrigerant receives heat from the high temperature portion of the Stirling refrigeration engine 30 and evaporates, condenses and radiates heat in the heat exchangers 62 and 63 to recover the cold heat is repeated. When the circulation pump 64 stops running, this cycle is stopped.

6 shows a fifth embodiment of the refrigerator of the present invention. Similarly to the second embodiment, the heat exchanger 62 for promoting evaporation of the drain and the heat exchanger 63 for preventing condensation of the freezer wall are connected in parallel, and the parallel connection structure is connected to the second high temperature side heat exchanger 61. And the circulation pump 64 in series. In the parallel connection structure, the valve 65 is connected in series to the upstream side of the heat exchange part 62, and the valve 66 is connected in series to the upstream side of the heat exchange part 63.

In the fifth embodiment, the defrosting refrigerant circulation circuit 80 is connected in parallel to the parallel connection structure of the heat exchange parts 62 and 63. The defrost refrigerant circulation circuit 80 includes a defrost heat exchanger 81 and valves 82 and 83 connected to upstream and downstream thereof. The defrost heat exchanger 81 transmits heat to the in-vehicle heat exchanger 42 by heat conduction or convection. Forced convection by a blowing fan may be generated between the defrost heat exchanger 81 and the in-chold heat exchanger 42. It is also possible to partition a part of the internal heat exchanger 42 for cooling inside the refrigerator and to configure the defrost heat exchanger 81.

Cooling of the cooling chambers 11, 12, 13 is performed with the valves 65, 66 open and the valves 82, 83 closed. When the stirling refrigeration engine 30 is driven, the low temperature side heat exchanger 41 loses heat, and the refrigerant inside flows into the internal heat exchanger 42 for cooling inside the low temperature side refrigerant circulation circuit 40 in a condensed state. .

The refrigerant flowing into the in-vehicle heat exchanger 42 evaporates with the heat of the air exiting the in-vehicle heat exchanger 42 to lower the surface temperature of the in-vehicle heat exchanger 42. The air exiting the in-vehicle cooling heat exchanger 42 is deprived of heat and becomes cold air, and is taken out from the cold air outlet 21 of the duct 20 to the cooling chambers 11, 12, 13, and the cooling chambers 11, 12. , Decrease the temperature of 13). Thereafter, the air is returned to the in-vehicle cooling heat exchanger 42 through a duct not shown.

The heat generated by the Stirling refrigeration engine 30, and the heat recovered from the inside of the low temperature portion become heat to be radiated from the high temperature portion. By this heat, the 1st high temperature side heat exchanger 51 and the 2nd high temperature side heat exchanger 61 are heated.

When the first high temperature side heat exchanger 51 is heated, part of the internal refrigerant evaporates, and the refrigerant flows into the heat exchanger 52 for heat dissipation in a gaseous form. The blower fan 53 blows out air on the surface of the heat exchanger 52 for heat dissipation, and the refrigerant in the gaseous phase takes heat away and condenses it. The refrigerant condensed to become a liquid phase is refluxed to the first high temperature side heat exchanger 51 and evaporated again. In this way, a cycle is repeated in which the refrigerant receives heat from the high temperature portion of the Stirling refrigeration engine 30, evaporates, and condenses it by transferring it to the cooling air in the heat radiating heat exchanger 52.

When the second high temperature side heat exchanger 61 is heated, part of the refrigerant inside evaporates and the refrigerant becomes a gas-liquid two-phase type. The refrigerant in the two gas-liquid phases is sent to the heat exchange parts 62 and 63 by the circulation pump 64 disposed at the most upstream portion of the second high temperature side refrigerant circulation circuit 60. The refrigerant flows through the heat exchange parts 62 and 63, and transfers heat to the drain vessel 26 to promote evaporation of the drain, and also heats to a part of the cooler wall in contact with the outside air, thereby reducing the temperature of this part to the dew point temperature. Keep above.

The coolant that recovers the cold heat from the drain in the heat exchange part 62 and the cold heat recovered from the housing 10 in the heat exchange part 63 has a gaseous phase but liquefies, and the second high temperature side heat exchanger is formed in a nearly liquid phase. Reflux to 61. Then, some evaporate and recover the gas-liquid phase 2 again. In this way, a cycle in which the refrigerant receives heat from the high temperature portion of the Stirling refrigeration engine 30 and evaporates, condenses and radiates heat in the heat exchangers 62 and 63 to recover the cold heat is repeated. Since the valves 82 and 83 are closed, the heat of the refrigerant is not transmitted to the internal heat exchanger 42 for cooling. When the circulation pump 64 stops running, this cycle is stopped.

When the surface temperature of the in-vehicle heat exchanger 42 decreases, the air exiting the in-vehicle heat exchanger 42 is deprived of heat and becomes cold air. At the same time, moisture contained in the air, that is, moisture penetrating into the cooling chambers 11, 12, 13, and moisture taken from the stored food in the cooling chamber are frosted and adhered to the internal heat exchanger 42 for cooling. If the frost is attached, the heat exchange efficiency between the air-cooling heat exchanger 42 and the air is lowered for the heat insulation action of the frost. If the gap between the fins of the in-vehicle heat exchanger 42 is narrowed by frost, the amount of ventilation is reduced. As a result, the cooling capacity is further lowered.

Thus, the valves 82 and 83 are opened at an appropriate timing so that the refrigerant exiting from the second high temperature side heat exchanger 61 flows to the defrost heat exchanger 81. Then, the heat of the refrigerant is transmitted to the internal cooling heat exchanger 42 to melt frost attached to the internal cooling heat exchanger 42. The molten frost becomes a drain and flows out to the drain container 26.

Cooling heat of the in-vehicle heat exchanger 42, mainly frost, is recovered as a refrigerant. The coolant is recovered, the temperature is lowered, and the refrigerant that has been liquefied is refluxed to the second high temperature side heat exchanger 61 to become a gas-liquid two-phase again. In order to increase the efficiency of defrosting and shorten the defrosting time, the valves 65 and 66 may be closed during the defrosting period so that the refrigerant flows in the defrost heat exchanger 81.

According to this configuration, the defrost of the in-vehicle heat exchanger 42 can be defrosted without providing the defrost heat transfer heater. In addition, since the cold heat of frost is recovered and the high temperature part of the Stirling refrigeration engine 30 is cooled, the heat load of the heat dissipation system is reduced, and the heat dissipation efficiency of the whole heat dissipation system is also improved.

Since the first high temperature side refrigerant circulation circuit 50 is a loop type thermosiphon, it is possible to discharge heat from the first high temperature side heat exchanger 51 without using artificial energy. In the other second high temperature side refrigerant circulation circuit 60, the refrigerant is transferred by the circulation pump 64 to promote the evaporation of the heat of the high temperature portion, to prevent condensation of the cooler wall, and to defrost the internal heat exchanger of the internal cooling chamber. It is surely available.

It is also possible to set it as the structure which connects the defrost heat exchanger 81 in series with the parallel connection structure of the heat exchange parts 62 and 63. FIG. In this case, the valves 82 and 83 become unnecessary. When the circulation pump 64 is operated with the valves 65 and 66 open, the evaporation promotion of the drain, the heating of the cooler wall, and the defrosting are simultaneously performed. Closing the valve 65 stops the evaporation promotion of the drain, and closing the valve 66 stops the heating of the cooler wall. When the circulation pump 64 is stopped, the operations of the heat exchange parts 62 and 63 and the defrost heat exchanger 81 are all stopped.

7 shows a sixth embodiment of the refrigerator of the present invention. 6th Embodiment adds the following element to 5th Embodiment. That is, the heat storage part 90 is provided between the parallel connection structure of the heat exchange part 62, the heat exchange part 63, and the defrost heat exchanger 81, and the 2nd high temperature side heat exchanger 61. As shown in FIG.

When the sterling refrigeration engine 30 is driven while the valves 65 and 66 are opened and the valves 82 and 83 are closed, the low temperature side heat exchanger 41 loses heat, and the refrigerant inside is condensed. Flow into the internal cooling heat exchanger (42). The refrigerant flowing into the in-vehicle heat exchanger 42 evaporates to lower the surface temperature of the in-vehicle heat exchanger 42. Thereby, cooling of the cooling chambers 11, 12, 13 is performed.

The other 1st high temperature side heat exchanger 51 and the 2nd high temperature side heat exchanger 61 are heated. When the first high temperature side heat exchanger 51 is heated, part of the internal refrigerant evaporates, and the refrigerant flows into the heat exchanger 52 for heat dissipation in a gaseous form. The blower fan 53 discharges air to the surface of the heat exchanger 52 for heat dissipation, and the refrigerant in the gas phase takes heat away and condenses it. The refrigerant condensed to become a liquid phase is refluxed to the first high temperature side heat exchanger 51 and evaporated again. In this way, a cycle is repeated in which the refrigerant receives heat from the high temperature portion of the stirling refrigeration engine 30 and evaporates, and condenses it by transferring it to the cooling air in the heat radiation heat exchanger 52.

When the second high temperature side heat exchanger 61 is heated, part of the refrigerant inside evaporates and the refrigerant becomes a gas-liquid two-phase type. The refrigerant in the two gas-liquid phases is sent to the heat exchange parts 62 and 63 by the circulation pump 64 disposed at the most upstream portion of the second high temperature side refrigerant circulation circuit 60. The refrigerant is separated and flows through the heat exchange parts 62 and 63, heat is transferred to the drain vessel 26 to promote evaporation of the drain, and heat is transferred to a part of the cooler wall in contact with the outside air, thereby converting the temperature of this part to the dew point temperature. Keep above.

The refrigerant leaving the heat exchange parts 62 and 63 passes through the heat storage part 90. The excess heat after heat dissipation in the heat exchange parts 62 and 63 is accumulated in the heat storage part 90. Although the refrigerant | coolant which gave extra heat to the heat storage part 90 was a gaseous phase, liquefaction advances and it returns to the 2nd high temperature side heat exchanger 61 in an almost liquid form. Then, some evaporate and recover the gas-liquid phase 2 again. In this way, the cycle is repeated when the refrigerant receives heat from the high temperature portion and evaporates, condenses and radiates heat in the heat exchange portions 62 and 63 and the heat storage portion 90 to recover the cold heat. Since the valves 82 and 83 are closed, the heat of the refrigerant is not transmitted to the internal heat exchanger 42 for cooling. When the circulation pump 64 stops running, this cycle is stopped.

When defrost of the in-chamber heat exchanger 42 is defrosted, the valves 82 and 83 are opened to allow the refrigerant released from the second high temperature side heat exchanger 61 to flow to the defrost heat exchanger 81. Then, the heat of the refrigerant is transmitted to the internal cooling heat exchanger 42 to melt frost attached to the internal cooling heat exchanger 42. The molten frost becomes a drain and flows out to the drain container 26.

Cooling heat of the in-vehicle heat exchanger 42, mainly frost, is recovered as a refrigerant. The coolant whose temperature is lowered by recovering the cooling heat exchanges heat with the heat storage unit 90 when passing through the heat storage unit 90. After dissipating the cooling heat and receiving the heat from the heat storage unit 90, the temperature is raised, and the refrigerant is refluxed to the second high temperature side heat exchanger 61 to become a gas-liquid two phase again. In order to increase the defrosting rate and shorten the defrosting time, the valves 65 and 66 are closed during the defrosting period so that the refrigerant flows in the defrost heat exchanger 81.

In this manner, the cold heat from the frost is accumulated in the heat storage unit 90 during the defrost process. When the defrost process is completed and the normal operation is returned, the heat storage unit 90 transmits cold heat to the refrigerant passing through and cools the high temperature portion of the stirling refrigeration engine 30. Instead, the heat storage unit 90 accumulates heat from the high temperature unit and is provided in the next defrost process.

According to this configuration, the defrost of the in-vehicle heat exchanger 42 can be defrosted without providing the defrost heat transfer heater. Even if the sterling refrigeration engine 30 is stopped, the coolant can be defrosted by heating the refrigerant by the heat accumulated in the heat storage unit 90 by simply driving the circulation pump 64.

Similarly to the fifth embodiment, since the cold heat of frost is recovered and the high temperature part of the Stirling refrigeration engine 30 is cooled, the heat load of the heat dissipation system is reduced, and the heat dissipation efficiency of the entire heat dissipation system is also improved. As a result, the operating COP of the stirling refrigeration engine 30 is improved, and power consumption can be reduced.

It is also possible to set it as the structure which connects the defrost heat exchanger 81 in series with the parallel connection structure of the heat exchange parts 62 and 63. FIG. In this case, the valves 82 and 83 become unnecessary. When the circulation pump 64 is operated with the valves 65 and 66 open, the evaporation promotion of the drain, the heating of the cooler wall, and the defrosting are simultaneously performed. Closing the valve 65 stops the evaporation promotion of the drain, and closing the valve 66 stops the heating of the cooler wall. When the circulation pump 64 is stopped, the operations of the heat exchange parts 62 and 63 and the defrost heat exchanger 81 are all stopped.

8 shows a seventh embodiment of the refrigerator of the present invention. The seventh embodiment differs from the second embodiment in that the high temperature side heat exchanger is of a single type. That is, in this embodiment, the single type high temperature side heat exchanger 71 is provided in the high temperature part of the Stirling refrigeration engine 30. As shown in FIG. A large number of fins are provided inside the high temperature side heat exchanger 71 so that heat can be efficiently exchanged with the refrigerant.

In the form containing this high temperature side heat exchanger 71, the 1st high temperature side refrigerant | circulation circuit 50 and the 2nd high temperature side refrigerant | circulation refrigerant circuit 60 are comprised. That is, the high temperature side heat exchanger 71 is a high temperature side heat exchanger common to both the first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60, and this common high temperature side heat exchanger ( The first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60 are connected to each other in parallel to 71.

9 shows an eighth embodiment of the refrigerator of the present invention. In an environment with high humidity, it is necessary to constantly promote the evaporation of the drain and to prevent the condensation on the freezer wall, but the piping structure of the eighth embodiment is suitable for such a case.

The eighth embodiment differs from the first embodiment in that the high temperature side heat exchanger is of a single type. That is, in this embodiment, the single type high temperature side heat exchanger 71 is provided in the high temperature part of the Stirling refrigeration engine 30. As shown in FIG. A large number of fins are provided inside the high temperature side heat exchanger 71 so that heat can be efficiently exchanged with the refrigerant.

In the form containing this high temperature side heat exchanger 71, the 1st high temperature side refrigerant | circulation circuit 50 and the 2nd high temperature side refrigerant | circulation refrigerant circuit 60 are comprised. That is, the high temperature side heat exchanger 71 is a high temperature side heat exchanger common to both the first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60, and this common high temperature side heat exchanger ( The first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60 are connected to each other in parallel to 71.

According to the above configuration, there is an advantage that the piping structure of the second high temperature side refrigerant circulation circuit 60 is simple and the number of assembling steps is reduced.

The positions of the heat exchange parts 62 and 63 may be reversed to first heat the cooler wall and then to heat the drain container 26.

10 shows a ninth embodiment of the refrigerator of the present invention. 9th Embodiment has a structure substantially the same as 8th Embodiment, but the following point differs from 8th Embodiment. That is, in the eighth embodiment, the reflux refrigerant pipe having a function of refluxing the refrigerant in the high temperature side heat exchanger 71 in the first high temperature side refrigerant circulation circuit 50 is connected to the high temperature side heat exchanger 71. In the ninth embodiment, the reflux refrigerant pipe is connected to the suction side of the circulation pump 64.

According to this configuration, the coolant flowing from the high temperature side heat exchanger (71) to the heat dissipation heat exchanger (52) in the form of natural circulation is returned to the high temperature side heat exchanger (71) when refluxed from the heat dissipation heat exchanger (52). It does not enter directly, but joins the refrigerant flowing through the second high temperature side refrigerant circulation circuit 60. For this reason, the amount of heat of the refrigerant having a saturation temperature refluxed from the heat exchanger heat exchanger 52 is added to the amount of heat of the refrigerant flowing out of the high temperature side heat exchanger 71 to the second high temperature side refrigerant circulation circuit 60. 2 The total heat amount of the refrigerant flowing through the high temperature side refrigerant circulation circuit 60 is increased. As a result, the amount of heat applied to the heat exchanger 62 for promoting evaporation of the drain and the heat exchanger 63 for preventing condensation of the freezer wall is increased, and the utilization efficiency of heat generated by the Stirling Refrigeration Engine 30 can be improved.

11 shows a tenth embodiment of the refrigerator of the present invention. 10th Embodiment is the same structure as 5th Embodiment, but differs from 5th Embodiment in that the high temperature side heat exchanger is unitary. By this structure, the defrost of the internal heat exchanger heat exchanger 42 can be defrosted like a 5th embodiment, without providing a defrosting heat transfer heater. In addition, since the cold heat of frost is recovered and the high temperature part of the Stirling refrigeration engine 30 is cooled, the heat load of the heat dissipation system is reduced, and the heat dissipation efficiency of the entire heat dissipation system is improved.

An eleventh embodiment of the refrigerator of the present invention is shown in FIG. 11th Embodiment is the same structure as 6th Embodiment, but differs from 6th Embodiment in that the high temperature side heat exchanger is unitary. In this configuration, as in the sixth embodiment, the defrosting heat exchanger 42 can be defrosted without the installation of the defrost heat transfer heater, but the sterling refrigeration engine 30 is stopped even if the circulating pump 64 is stopped. ), The frost can be removed by heating the refrigerant with the heat accumulated in the heat storage unit 90.

13 shows a twelfth embodiment of the refrigerator of the present invention. 12th Embodiment changed the structure of 2nd Embodiment as follows. That is, in the case of the second embodiment, the first high temperature side heat exchanger 51 is transferred to the first high temperature side refrigerant circulation circuit 50, and the second high temperature side heat exchanger 61 is the second high temperature side refrigerant circulation circuit. Was assigned to (60). In the twelfth embodiment, both of the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61 are common to the first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60. Used as

As shown in Fig. 13, the refrigerant pipe of the first high temperature side refrigerant circulation circuit 50 exits in parallel from both the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61, and joins on the way. Then, it enters the heat exchanger 52 for heat dissipation. The refrigerant pipe leaving the heat dissipation heat exchanger 52 branches in the middle, and returns to the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61 in parallel.

The refrigerant pipe of the second high temperature side refrigerant circulation circuit 60 exits in parallel from both of the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61, joins in the middle, and enters the circulation pump 64. . The refrigerant pipe exiting the parallel connection structure of the heat exchanger 62 for promoting evaporation of the drain and the heat exchanger 63 for preventing condensation of the freezer wall is branched in the middle, and the first high temperature side heat exchanger 51 is formed in parallel. And the second high temperature side heat exchanger (61).

In other words, the first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60 are parallel to each other for each of the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61. Is connected.

By the above configuration, the refrigerant is supplied to the first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60 from both the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61. Is supplied. In addition, the refrigerant is refluxed from the first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60 for both the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61. do.

According to this configuration, the first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60 are respectively applied to the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61. Since it connects in parallel with each other, even if any one of the 1st high temperature side heat exchanger 51 and the 2nd high temperature side heat exchanger 61 is removed, multiple high temperature side refrigerant | circulation circuits will be ensured. As a result, the circuit becomes unavailable and the refrigerant circulation stops, and as a result, it is easy to avoid the situation such that the Stirling refrigeration engine 30 is damaged by poor heat radiation.

In addition, in both the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61, the refrigerant is supplied to the first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60. Since supply and reflux are performed, both the 1st high temperature side heat exchanger 51 and the 2nd high temperature side heat exchanger 61 can be involved in the heat supply to the outside and the recovery of cold heat from the outside.

The thirteenth embodiment of the refrigerator of the present invention is shown in FIG. 13th Embodiment changed the structure of 8th Embodiment as follows. That is, in the eighth embodiment, a single type high temperature side heat exchanger 71 is used. In the thirteenth embodiment, a split type high temperature side heat exchanger, that is, a first high temperature side heat exchanger 51 and a second high temperature side heat exchanger, is used. 61 is used.

As shown in Fig. 14, the refrigerant pipe of the first high temperature side refrigerant circulation circuit 50 exits in parallel from both the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61, and joins on the way. Then, it enters the heat exchanger 52 for heat dissipation. The refrigerant pipe leaving the heat dissipation heat exchanger 52 branches in the middle, and returns to the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61 in parallel.

The refrigerant pipe of the second high temperature side refrigerant circulation circuit 60 exits in parallel from both of the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61, joins in the middle, and enters the circulation pump 64. . After passing through the heat exchanger 62 for promoting evaporation of the drain, the refrigerant pipe exiting the heat exchanger 63 for preventing condensation of the freezer wall is branched in the middle, and the first high temperature side heat exchanger 51 is formed in parallel. And the second high temperature side heat exchanger (61).

In other words, the first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60 are parallel to each other for each of the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61. Is connected.

By the above configuration, the refrigerant is supplied to the first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60 from both the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61. Is supplied. In addition, the refrigerant is refluxed from the first high temperature side refrigerant circulation circuit 50 and the second high temperature side refrigerant circulation circuit 60 for both the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61. do.

15 shows a fourteenth embodiment of the refrigerator of the present invention. 14th Embodiment changes the structure of 9th Embodiment as follows. That is, in the ninth embodiment, a single type high temperature side heat exchanger 71 is used. In the thirteenth embodiment, a split type high temperature side heat exchanger, that is, a first high temperature side heat exchanger 51 and a second high temperature side heat exchanger, is used. 61 is used.

As shown in Fig. 15, the refrigerant pipe of the first high temperature side refrigerant circulation circuit 50 exits in parallel from both the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61, and joins on the way. Then, it enters the heat exchanger 52 for heat dissipation. The reflux refrigerant pipe leaving the heat dissipation heat exchanger 52 is connected to the suction side of the circulation pump 64.

The refrigerant pipe of the second high temperature side refrigerant circulation circuit 60 exits in parallel from both the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61, joins in the middle, and enters the circulation pump 64. . After passing through the heat exchanger 62 for promoting evaporation of the drain, the refrigerant pipe exiting the heat exchanger 63 for preventing condensation of the freezer wall is branched in the middle, and the first high temperature side heat exchanger 51 is formed in parallel. And the second high temperature side heat exchanger (61).

When the first high temperature side refrigerant circulation circuit 50 is closed, the second high temperature side refrigerant circulation circuit 60 causes the refrigerant circulation of the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61 to be blocked. As a matter of course, the refrigerant circulation in the first high temperature side refrigerant pipe 50 may be carried out by the first high temperature side heat exchanger 51 even when the circulation pump 64 fails or cannot transfer the refrigerant therefrom. And the type that flows back the refrigerant pipe from the second high temperature side heat exchanger 61 to the circulation pump 64. As a result, the circuit becomes unavailable and the refrigerant circulation stops, and as a result, it is easy to avoid the situation such that the Stirling refrigeration engine 30 is damaged by poor heat radiation.

16 shows a fifteenth embodiment of the refrigerator of the present invention. In the fifteenth embodiment, the defrosting refrigerant circulation circuit 80 is connected in parallel to the parallel connection structure of the heat exchange parts 62 and 63 as in the fifth embodiment and the tenth embodiment. The defrost refrigerant circulation circuit 80 includes a defrost heat exchanger 81 and valves 82 and 83 connected to upstream and downstream thereof. The defrost heat exchanger 81 transfers heat to the cooling heat exchanger 42 for cooling in the refrigerator by heat conduction or convection or by forced convection by a blowing fan.

According to this configuration, the defrost of the in-vehicle heat exchanger 42 can be defrosted without providing the defrost heat transfer heater. Furthermore, since the cold heat of frost is recovered and the high temperature part of the Stirling refrigeration engine 30 is cooled, the heat load of the heat dissipation system is reduced, and the heat dissipation efficiency of the whole heat dissipation system is also improved. As a result, the operating COP of the stirling refrigeration engine 30 is improved, and power consumption can be reduced.

17 shows a sixteenth embodiment of the refrigerator of the present invention. 16th Embodiment adds the following element to 15th Embodiment. That is, the sixth implementation between the parallel connection structure of the heat exchanger 62, the heat exchanger 63, and the defrost heat exchanger 81 and the first high temperature side heat exchanger 51 and the second high temperature side heat exchanger 61. As in the form and the eleventh embodiment, a heat storage unit 90 is provided.

According to this configuration, the defrosting heat exchanger 42 can be defrosted without the installation of a defrosting heat heater, but the circulating pump 64 is driven even if the stirling refrigeration engine 30 is stopped. In this case, defrosting can be performed by heating the refrigerant with the heat accumulated in the heat storage unit 90.

As mentioned above, although each embodiment of this invention was described, the scope of the present invention is not limited to this, A various change can be added and implemented in the range which does not deviate from the main point of invention.

The present invention is a refrigerator for home use or business use, and can be applied to the overall use of a stirling refrigerator as a cold heat source.

Claims (15)

In the refrigerator which performs in-vehicle cooling by a Stirling refrigeration engine, A cooler for transferring the heat of the high temperature portion of the stirling refrigeration engine to the refrigerant in the gas-liquid two-phase, and used for at least one of promoting the evaporation of the drain, preventing condensation of the cooler wall and defrost of the heat exchanger for cooling in the refrigerator. In the refrigerator which performs in-vehicle cooling by a Stirling refrigeration engine, A first high temperature side refrigerant circulation circuit for dissipating the heat of the hot portion of the stirling refrigeration engine to the outside, and the heat of the hot portion to at least one of a dehumidification of the heat exchanger for promoting evaporation of the drain, preventing condensation of the cooler wall, and cooling in the refrigerator. A refrigerator for forming a second high temperature side refrigerant circulation circuit to be used. The refrigerator according to claim 2, wherein the first high temperature side refrigerant circulation circuit and the second high temperature side refrigerant circulation circuit are independent of each other. The refrigerator according to claim 3, wherein the first high temperature side refrigerant circulation circuit circulates the refrigerant by natural circulation, and the second high temperature side refrigerant circulation circuit circulates the refrigerant by forced circulation. In the refrigerator which performs in-vehicle cooling by a Stirling refrigeration engine, A high temperature side heat exchanger installed at a high temperature portion of the stirling refrigeration engine, a heat dissipation heat exchanger for dissipating heat to an outside environment, and a first high temperature side refrigerant, a loop type thermosiphon formed between the high temperature side heat exchanger and the heat exchanger. A second high temperature side refrigerant circulation circuit which uses the heat of the high temperature portion for at least one of promoting the evaporation of the drain, preventing condensation on the freezer walls, and defrosting the internal heat exchanger for cooling the inside, and a refrigerant in the high temperature side heat exchanger. And a circulation pump for feeding the second high temperature side refrigerant circulation circuit. In the refrigerator which performs in-vehicle cooling by a Stirling refrigeration engine, A first high temperature side refrigerant circulation circuit for dissipating the heat of the hot portion of the stirling refrigeration engine to the outside, and the heat of the hot portion to at least one of a defrost of the heat exchanger for promoting evaporation of the drain, preventing condensation of the cooler wall, and cooling in the refrigerator. A cooler for forming a second high temperature side refrigerant circulation circuit to be used and simultaneously connecting the first high temperature side refrigerant circulation circuit and the second high temperature side refrigerant circulation circuit to a common high temperature side heat exchanger provided in the high temperature portion in parallel. 7. The refrigerator according to claim 6, wherein a plurality of said high temperature side heat exchangers are provided and a first high temperature side refrigerant circulation circuit and a second high temperature side refrigerant circulation circuit are connected in parallel to each other for each of said plurality of high temperature side heat exchangers. . 6. The refrigerator according to claim 5, wherein a reflux refrigerant pipe of said first high temperature side refrigerant circulation circuit is connected to a suction side of said circulation pump. The refrigerator according to any one of claims 2 to 8, wherein the refrigerant is used as a gas-liquid two-phase type in one or both of the first high temperature side refrigerant circulation circuit and the second high temperature side refrigerant circulation circuit. In the refrigerator which performs in-vehicle cooling by a Stirling refrigeration engine, The heat exchanger is installed in parallel with the heat exchanger to promote evaporation of the drain and the heat exchanger is installed in order to prevent condensation of the freezer wall. The parallel connection structure is connected in series with the heat exchanger installed at the high temperature of the stirling refrigeration engine. Cooler to form a circulation circuit. In the refrigerator which performs in-vehicle cooling by a Stirling refrigeration engine, And a heat exchanger installed in the high temperature portion of the stirling refrigeration engine, a heat exchanger installed to promote evaporation of the drain, and a heat exchanger installed in series to prevent condensation of the cooler wall, thereby forming a high-temperature refrigerant circulation circuit. The method according to any one of claims 1 to 8, 10 or 11, A low temperature refrigerant circulation circuit including a heat exchanger installed at a low temperature portion of the stirling refrigeration engine and a heat exchanger for internal cooling is formed, and a defrost heat exchanger is provided for the internal cooling heat exchanger, and the defrost heat exchanger and the stirling are provided. A refrigerator for forming a high temperature side refrigerant circulation circuit including a heat exchanger installed in a high temperature portion of a refrigeration engine. The refrigerator according to claim 12, wherein a heat storage unit is provided in a high temperature side refrigerant circulation circuit including a heat exchanger installed in the defrost heat exchange unit and a high temperature unit of the stirling refrigeration engine. The low temperature refrigerant circulation circuit including a heat exchanger installed at a low temperature portion of the Stirling refrigeration engine and a heat exchanger for internal cooling is formed, and a defrost heat exchanger is provided for the internal cooling heat exchanger. And a high temperature side refrigerant circulation circuit including a commercial heat exchanger and a heat exchanger installed at a high temperature portion of the stirling refrigeration engine. 15. The refrigerator according to claim 14, wherein a heat storage unit is provided in a high temperature side refrigerant circulation circuit including a heat exchanger installed in the defrost heat exchange unit and a high temperature unit of the Stirling refrigeration engine.

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