JP3756503B2 - Refrigerator and its operating method - Google Patents

Description

  The present invention relates to a refrigerator having a cooling space for cooling stored items and an operation method thereof.

  Conventionally, a vapor compression refrigeration engine has been widely used in general refrigerators. This vapor compression refrigeration engine obtains a low temperature by using condensation and evaporation of Freon gas. Fluorocarbon is a substance that is very easy to use as a refrigerant because it has neither flammability nor explosiveness and low corrosivity. However, chlorofluorocarbon gas has a high chemical stability, and thus when it is released into the atmosphere, it has a problem that it reaches the stratosphere and destroys the ozone layer. For this reason, in recent years, specific chlorofluorocarbons and alternative chlorofluorocarbons are used, and the production of chlorofluorocarbons is regulated worldwide.

  Therefore, in recent years, the Stirling refrigeration engine has attracted attention as a cooling technique that replaces the vapor compression refrigeration engine using chlorofluorocarbon gas as a refrigerant. The Stirling refrigeration engine reciprocates a piston and a displacer with an arbitrary phase difference by external power such as a motor. Thereby, compression and expansion of the working gas are repeated. As a result, a cold head (low temperature part) and a worm head (high temperature part) are configured. The cold head provides a low temperature.

In a Stirling refrigerating engine, a gas that does not adversely affect the global environment, such as helium, hydrogen gas, or nitrogen gas, can be used as the working gas.
JP-A 63-163755 JP-A-11-166784 JP-A-11-212325

  If it is a refrigerator equipped with the above Stirling refrigeration engine, the heat from the inside is taken away by the cold head, and the heat is discharged from the warm head to the outside as waste heat. Cooling can be performed.

  However, a refrigerator equipped with a Stirling refrigeration engine has the same problem as a conventional general refrigerator. That is, the above refrigerator has a problem that when the ambient environment is high humidity, dew condensation occurs in a portion (such as a door packing area or a wall surface outside the chamber) that becomes cooler than the ambient environment due to cool air inside the refrigerator. .

  Conventionally, a refrigerator that prevents the condensation by heating the portion where the condensation occurs with an electric heater has been proposed. However, such a configuration has a problem that power consumption increases.

  In addition, the inventors of the present application have examined a refrigerator capable of preventing dew condensation generated on the outer wall and draining as a refrigerator for solving the above-described problems. This refrigerator is configured to forcibly guide the liquid portion of the refrigerant used for cooling the worm head of the Stirling refrigerator to a dew condensation prevention pipe installed near the outer wall or a drain treatment pipe installed below the refrigerator.

  In the dew condensation prevention pipe as described above, a liquid phase fluid such as water is enclosed. Therefore, the gas phase for discharging heat to the outside and the liquid phase for preventing condensation are in a two-layer state. The forced circulation of the liquid phase fluid is performed using a circulation pump.

  In the above-mentioned forced circulation, when the ambient temperature rises when the operation of the circulation pump is stopped for a predetermined time, the temperature of the liquid phase fluid rises accordingly. As a result, part of the liquid phase fluid remaining in the condensation prevention pipe may be gasified. Bubbles generated by gasification of the liquid phase fluid stay in the liquid phase condensation prevention pipe and / or the circulation pump for preventing condensation. As a result, there is a problem that the liquid phase fluid cannot be circulated properly even if the circulation pump is operated.

  The present invention has been made in view of the above problems, and its purpose is to eliminate a bubble generated in a liquid-phase dew condensation prevention pipe when the operation of the freezer has been stopped for a long time. It is an object of the present invention to provide a refrigerator and a method of operating the same, in which the problem that the liquid phase fluid is not properly circulated by the liquid phase circulation pump during the operation is solved.

  The refrigerator according to the present invention is as follows.

The cooler includes a cooling chamber in which an object to be cooled is stored, a low temperature portion that generates cool air for cooling the cooling chamber, and a high temperature portion that releases heat generated due to the generation of the cool air. And a liquid phase circulation circuit that is connected to the high temperature part and through which the liquid phase fluid flows, a liquid phase circulation pump that is provided in the liquid phase circulation circuit and circulates the liquid phase fluid, and can apply pressure to the liquid phase fluid Pressurizing means. The pressurizing means is one in which the high temperature part pressurizes by applying heat to the liquid phase fluid and / or the gas phase fluid, or has a heat source provided separately from the high temperature part, It is a heating means capable of applying heat from a heat source.

  According to this configuration, bubbles generated in the liquid phase fluid disappear when the operation of the freezer is stopped for a long time due to pressurization of the liquid phase fluid by the pressurizing means. As a result, the inconvenience that the liquid phase circulation pump runs idle at the start of the operation of the freezer and the liquid phase fluid does not circulate in the liquid phase circulation circuit is prevented.

  Note that the refrigerator may include a circulation circuit that connects the high-temperature part and the condenser and liquefies the vapor-phase fluid that has been vaporized by receiving heat from the high-temperature part.

  In the operation method of the present invention, in the above-described refrigerator, the gas phase fluid is added to the gas phase fluid during normal operation during the period from the start of operation until the liquid phase fluid is properly circulated by the liquid phase circulation pump. Apply a pressure higher than the applied pressure, ie high pressure.

  According to the above method, bubbles generated in the liquid phase fluid disappear when the operation of the freezer is stopped for a long time due to pressurization to the liquid phase fluid. As a result, the inconvenience that the liquid phase circulation pump runs idle at the start of the operation of the freezer and the liquid phase fluid does not circulate in the liquid phase circulation circuit is prevented.

  The aforementioned high pressure may be created by operating the cooler and setting the high temperature part to a higher temperature than during normal operation. Further, the above-described high pressure may be created by operating a heating means provided separately from the high-temperature part and setting the gas phase fluid to a higher temperature than usual.

  In addition, in order to execute the above-described method, the freezer is provided in the circulation circuit, and can apply pressure to the liquid phase fluid via the gas-liquid separation unit by applying pressure to the gas phase fluid. Means can also be provided. The pressurizing means can be realized by controlling the high temperature part to a temperature higher than that during normal operation, or has a heat source provided separately from the high temperature part, and is a liquid phase fluid and / or gas phase. It can also be realized by heating with a heating means capable of applying heat to the fluid.

  Further, the cooler includes a control device that controls the cooler, and the control device performs a cooling process between the start of operation of the cooler and the time when the liquid-phase circulation pump appropriately circulates the liquid-phase fluid. This can also be realized by executing a control for operating the piston of the cooler at a high speed or a control for increasing the stroke of the piston of the cooler so that the high temperature part becomes a predetermined temperature higher than that during normal operation. it can.

  A refrigerator according to another aspect of the present invention releases a heat generated due to the generation of cold air, a cooling chamber in which an object to be cooled is stored, a low temperature portion that generates cold air for cooling the cooling chamber, and A cooler having a high-temperature part, a liquid-phase circulation circuit connected to the high-temperature part and through which the liquid-phase fluid flows, a liquid-phase circulation pump provided in the liquid-phase circulation circuit and circulating the liquid-phase fluid, a cooler and a liquid And a control device for controlling the phase circulation pump.

  In the above-described configuration, if the liquid-phase circulation pump is started on the condition that a predetermined time has elapsed since the start of the operation of the cooler by the control device, the temperature of the high-temperature part of the cooler is maintained until the predetermined time. Pressure is applied to the liquid phase fluid due to the rise. Thereby, the liquid phase fluid exerts pressure on the bubbles. As a result, bubbles remaining in the liquid phase circulation circuit can be eliminated. Thereafter, the liquid phase circulation pump is started. Therefore, it is possible to suppress the generation of noise due to the disappearance of bubbles in the liquid phase circulation circuit caused by the rapid activation of the circulation pump.

  Further, in the above configuration, if the output of the liquid-phase circulation pump is increased on the condition that a predetermined time has elapsed since the start of the operation of the cooler by the control device, from the start of the cooler to the normal operation In the meantime, the flow rate of the liquid phase fluid circulating in the liquid phase circulation circuit can be reduced. As a result, it is possible to reduce the noise generated by the disappearance of the bubbles in the liquid phase circulation circuit caused by the rapid activation of the circulation pump.

  A refrigerator according to still another aspect of the present invention releases a heat generated due to the generation of cold air, a cooling chamber in which an object to be cooled is stored, a low temperature portion that generates cold air for cooling the cooling chamber, and A cooler having a high-temperature part, a liquid-phase circulation circuit that is provided along the inner surface of the housing, is connected to the high-temperature part and through which the liquid-phase fluid flows, and is provided in the liquid-phase circulation circuit. A liquid phase circulation pump that circulates the liquid, a control device that controls the cooler and the liquid phase circulation pump, and a temperature sensor that measures the temperature of the surface of the housing or the liquid phase circulation circuit. Further, the control device activates the liquid phase circulation pump or increases the output of the liquid phase circulation pump on condition that the temperature detected by the temperature sensor has decreased.

  According to said structure, it becomes possible to start a liquid phase circulation pump, after the temperature of a liquid phase fluid falls and the bubble in a liquid phase circulation circuit lose | disappears by condensation. Therefore, it is possible to suppress the generation of noise caused by the disappearance of bubbles generated by the rapid activation of the circulation pump.

  In addition, it is desirable that the refrigerator further includes a humidity sensor that measures humidity near a predetermined position. In addition, when the humidity value measured by the humidity sensor becomes equal to or higher than a predetermined value, the control device preferably makes the output of the liquid phase circulation pump smaller than the output at the current stage or stops the circulation pump. .

  According to the above configuration, as the temperature of the liquid phase fluid in the circulation pipe rises as the temperature of the high temperature part rises, the dew point of the atmosphere around the liquid phase circulation circuit rises, so the vicinity of the liquid phase circulation circuit It is possible to suppress the occurrence of condensation on the surface.

  The refrigerator according to yet another aspect of the present invention releases a heat generated due to the generation of cold air and a cooling chamber in which an object to be cooled is stored, a low temperature portion that generates cold air for cooling the cooling chamber, and A cooler having a high-temperature part, a liquid-phase circulation circuit that is connected to the high-temperature part and through which the liquid-phase fluid flows, a liquid-phase circulation pump that is provided in the liquid-phase circulation circuit and circulates the liquid-phase fluid, A radiator for lowering the temperature, a radiator fan provided in the vicinity of the radiator, a cooler, a liquid phase circulation pump, and a controller for controlling the radiator fan are provided. In addition, after starting the cooler and before starting the liquid phase circulation pump, the control device stops the heat dissipating fan or outputs a smaller output than after starting the liquid phase circulation pump. To drive the heat dissipation fan.

  According to said structure, before starting a liquid phase circulation pump, the temperature of a liquid phase fluid can be made high by the raise of the temperature of a high temperature part compared with after starting a liquid phase circulation pump. . Thereby, the bubbles in the liquid phase circulation circuit disappear due to the pressure of the liquid phase fluid. Thereafter, the circulation pump is started. As a result, the generation of noise due to the disappearance of bubbles in the liquid phase circulation circuit is suppressed.

  According to the present invention, bubbles generated in the liquid phase fluid can be eliminated when the operation of the freezer has been stopped for a long time. As a result, the inconvenience that the liquid phase circulation pump runs idle at the start of the operation of the freezer and the liquid phase fluid does not circulate in the liquid phase circulation circuit is prevented.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(Embodiment 1)
FIG. 1 is a cross-sectional view illustrating a schematic configuration of a refrigerator according to the present embodiment. FIG. 2 is a diagram showing a piping configuration of the refrigerator of the present embodiment. The refrigerator 1 is for food preservation and includes a housing 10 having a heat insulating structure. Inside the housing 10, cooling chambers 11, 12, and 13 are provided that are partitioned into upper and lower three stages.

  Each of the cooling chambers 11, 12, and 13 has an opening on the front side of the housing 10 (left side as viewed in FIG. 1). This opening is closed by heat-insulating doors 14, 15, 16 that can be freely opened and closed. On the back surfaces of the heat insulating doors 14, 15, 16, packings 17 are mounted so as to surround the openings of the cooling chambers 11, 12, 13, respectively. Inside the cooling chambers 11, 12, and 13, shelves 18 suitable for the type of food to be stored are installed as appropriate.

  A cooling system and a heat dissipation system having the Stirling refrigeration engine 30 as a central element are disposed from the upper surface to the rear surface and further to the lower surface of the housing 10. A machine room 19 is provided at one corner of the upper and rear surfaces of the housing 10, and the Stirling refrigeration engine 30 is provided with the machine room 19. A part of the Stirling refrigeration engine 30 forms a cold head when driven. In addition, a wall surface temperature sensor 82 and a wall surface humidity sensor 81 are provided in the wall on the back side of the cooling chamber (on the right side as viewed in FIG. 1). The wall surface temperature sensor 82 can measure the temperature in the vicinity of the back surface of the cooling chamber and in the vicinity of the dew condensation prevention pipe 62 described later, and the wall surface humidity sensor 81 is in the vicinity of the back surface of the cooling chamber, In addition, it is possible to measure the humidity in the vicinity of the dew condensation prevention pipe 62 described later. Information measured by each of the wall surface temperature sensor 82 and the wall surface humidity sensor 81 is transmitted to a control device 90 (to be described later) through a signal line.

A low temperature side condenser 41 is attached to the cold head. In addition, a low-temperature evaporator 42 is installed in the back (back side) of the cooling chamber 13. The low temperature side condenser 41 and the low temperature side evaporator 42 are connected via refrigerant piping, and the low temperature side circulation circuit 40 is comprised by both. A natural medium such as CO ₂ is enclosed in the low temperature side circulation circuit 40, and cold heat is transferred by the low temperature side evaporator 42 and the low temperature side condenser 41.

  Inside the housing 10, a duct 20 for distributing the cold air obtained by the low temperature side evaporator 42 to the cooling chambers 11, 12, 13 is provided. The duct 20 has a cold air outlet 21 communicating with the cooling chambers 11, 12, and 13 at appropriate positions. In addition, a blower fan 22 for forcibly sending cool air is provided in the duct 20 at an appropriate place.

  Although not shown, a duct that collects air from the cooling chambers 11, 12, and 13 is provided inside the housing 10. The duct has a communication port below the low-temperature side evaporator 42, and the air to be cooled is supplied to the low-temperature side evaporator 42 as indicated by a broken line arrow B in FIG.

  The other part of the Stirling refrigeration engine 30 forms a worm head when driven. A high temperature side evaporator (high temperature part) 51 is attached to the worm head. The high temperature side evaporator 51 is provided with a temperature sensor 55 as shown in FIG. Further, a high temperature side condenser 52 and a heat radiating fan 110 are provided on the upper surface (see FIG. 1) of the housing 10 to radiate heat to the outside environment. The high temperature side evaporator (high temperature part) 51 and the high temperature side condenser 52 are connected via refrigerant piping, and the high temperature side natural circulation circuit 50 is comprised by both. The heat radiating fan 110 promotes heat exchange between the high temperature side condenser 52 and the outside air by the air flow generated by the rotation.

  Water (including an aqueous solution) or a hydrocarbon-based natural medium is enclosed in the high temperature side natural circulation circuit 50, and the natural medium naturally circulates in the high temperature side natural circulation circuit 50.

  On the other hand, the high temperature side evaporator (high temperature part) 51 is also connected to the high temperature side forced circulation circuit 60. The high temperature side forced circulation circuit 60 includes a circulation pump 61 for forcedly circulating the refrigerant and dew condensation prevention pipes 62, 63 and 64. Condensation prevention pipes 62, 63, 64 are partly provided at the openings of cooling chambers 11, 12, 13.

  Condensation is prevented by heating the vicinity of the opening where condensation is likely to occur (periphery of the contact portion between the packing 17 and the housing 10, that is, the boundary region between the interior and the exterior) with the heat of the refrigerant. Note that an electric heater 70 that generates heat by energization is attached to a place where condensation is expected to occur where the high-temperature forced circulation circuit 60 cannot be disposed due to manufacturing reasons.

  Then, operation | movement of the refrigerator 1 which consists of the said structure is demonstrated. When the Stirling refrigeration engine 30 is driven in the refrigerator 1 having the above-described configuration, the temperature of the cold head decreases. Therefore, the low temperature side condenser 41 is cooled, and the internal refrigerant is condensed.

  The refrigerant condensed in the low temperature side condenser 41 flows into the low temperature side evaporator 42 through the low temperature side circulation circuit 40. The refrigerant flowing into the low temperature side evaporator 42 is evaporated by the heat of the airflow passing outside the low temperature side evaporator 42, and the surface temperature of the low temperature side evaporator 42 is lowered.

  Therefore, the air passing through the vicinity of the low-temperature side evaporator 42 becomes cold air, and is blown out from the cold air outlet 21 of the duct 20 to the cooling chambers 11, 12, 13, and the temperature of the cooling chambers 11, 12, 13 is lowered. Thereafter, the air in the cooling chambers 11, 12, and 13 is returned to the vicinity of the low-temperature evaporator 42 through a duct (not shown) due to the airflow generated by the rotation of the blower fan 22.

  Note that the refrigerant evaporated in the low-temperature side evaporator 42 returns to the low-temperature side condenser 41 through the low-temperature side circulation circuit 40, and is decondensed again by removing heat. Then, the heat exchange operation described above is repeated.

  On the other hand, as shown in FIG. 2, the heat generated by driving the Stirling refrigeration engine 30 and the heat recovered from the interior by the worm head are dissipated from the worm head as waste heat. Therefore, the high temperature side evaporator (high temperature part) 51 is heated, and the internal refrigerant evaporates.

  The gas phase refrigerant evaporated in the high temperature side evaporator (high temperature part) 51 flows through the high temperature side natural circulation circuit 50 and into the high temperature side condenser 52 provided above. The refrigerant that has flowed into the high temperature side condenser 52 is condensed by the heat dissipation fan 110 being deprived of heat by the airflow introduced from the outside of the warehouse into the high temperature side condenser 52. The refrigerant condensed in the high temperature side condenser 52 returns to the high temperature side evaporator (high temperature part) 51 through the high temperature side natural circulation circuit 50, receives heat, and evaporates again. Then, the heat exchange operation described above is repeated.

  Of the refrigerant saturated in the high-temperature side evaporator (high-temperature part) 51, the liquid-phase refrigerant is forcibly circulated to the high-temperature side forced circulation circuit 60 by the circulation pump 61, and the condensation prevention pipes 62, 63, 64. Accordingly, the vicinity of the openings of the cooling chambers 11, 12, 13 is heated by the heat of the introduced refrigerant.

  By adopting such a configuration, it is possible to keep the temperature in the vicinity of the opening where condensation is likely to occur at a temperature equal to or higher than the dew point temperature and prevent condensation without requiring unnecessary power. It should be noted that, in a portion where condensation is expected to occur where the high-temperature side forced circulation circuit 60 cannot be disposed, the electric heater 70 is energized, so that the temperature can be kept above the dew point temperature and condensation can be prevented.

  Here, as shown in FIG. 3, the refrigerator 1 of the present embodiment includes a dew condensation detection unit 80 that determines the degree of dew condensation in the vicinity of the opening based on the ambient temperature and humidity, and the dew condensation detection. Based on the detection result of the unit 80, the heat dissipation fan 110, the circulation pump 61, and the control device 90 that controls the electric heater 70 are included.

  This control device is characterized in that it controls the refrigerant circulation amount of the high temperature side forced circulation circuit 60 and the heat release amount from the high temperature side natural circulation circuit 50 according to the possibility of condensation. Further, a signal indicating the temperature detected by the temperature sensor 55 for measuring the temperature of the high temperature side evaporator (high temperature part) 51 is transmitted to the control device 90, and the control device 90 performs Stirling based on the signal. The operation of the refrigeration engine 30 is configured to be controlled.

  Specifically, if the control device 90 determines that there is a high possibility of condensation near the opening based on the detection result of the condensation detection unit 80, the controller 90 operates the circulation pump 61 and energizes the electric heater 70. When it is determined that the possibility of condensation is low, the operation of the circulation pump 61 and the energization of the electric heater 70 are stopped.

  By adopting such a configuration, when the possibility of dew condensation in the vicinity of the opening is low, the outer wall surface is not unnecessarily heated. Therefore, it is possible to reduce the power consumption while suppressing the heat load on the interior. For example, when the surrounding environment is high temperature and low humidity, the load required for cooling increases and the worm head becomes high temperature.

  However, the amount of refrigerant circulating in the high-temperature side forced circulation circuit 60 is reduced by the above control. As a result, it is possible to appropriately prevent condensation without heating the outer wall surface. If the configuration as described above is employed, the operation time of the circulation pump 61, which is a mechanical element that is relatively susceptible to failure, is reduced, which can contribute to improving the reliability of the refrigerator.

  In addition, when the control device 90 determines that the possibility of condensation near the opening is high based on the detection result of the dew condensation detection unit 80, the blast volume of the Stirling refrigeration engine 30 and the heat radiating fan 110 simultaneously with the above control. (In other words, the amount of heat released from the high-temperature side natural circulation circuit 50) is reduced, and control is performed so that the difference between the surface temperature of the worm head and the ambient temperature becomes a predetermined value or more. The temperature difference equal to or greater than the predetermined value is a value obtained in advance by experiments so that the refrigerant temperature passing through the dew condensation prevention pipes 62, 63, 64 is equal to or higher than the ambient temperature.

  By adopting such a configuration, even when the load on the Stirling refrigerating engine 30 is small (for example, when the ambient environment is low temperature and high humidity), the cooling temperature of the high temperature side forced circulation circuit 60 is predetermined. Maintained above value. As a result, the dew condensation prevention pipes 62, 63, 64 can always function.

  As shown in FIGS. 2 and 3, the dew condensation detection unit 80 measures the wall humidity at a location where condensation is relatively likely to occur (around the dew condensation prevention pipes 62, 63, 64, etc.). It is desirable to have At this time, for example, the control device 90 preferably determines that the possibility of condensation is high if the relative humidity is 90% or higher, and determines that the possibility of condensation is low if the relative humidity is less than 90%.

  By adopting such a configuration, the control device 90 can directly determine the possibility of condensation according to the relative humidity in the vicinity of the outer wall surface. As a result, it is possible to detect condensation at an early stage with a simple configuration.

  Further, temperature information and humidity information in the vicinity of the dew condensation prevention pipe 62 acquired by the wall surface temperature sensor 82 and the wall surface humidity sensor 81 are transmitted to the control device 90. Based on the temperature information and humidity information, the control device 90 can control the heat radiating fan 110, the electric heater 70, the circulation pump 61, and the Stirling refrigeration engine 30.

  Next, a method of applying pressure to the gas-phase fluid will be described with reference to FIGS. 4 to 6 in order to eliminate bubbles generated in the liquid-phase fluid in the condensation prevention pipe of the present embodiment.

  As can be seen from FIG. 4, the high-temperature side evaporator 51 of the above-described refrigerator has a liquid phase on the lower side and a gas phase on the upper side, and functions as a gas-liquid separation unit. Therefore, normally, bubbles generated on the liquid phase side rise and are released to the gas phase side. As a result, the liquid phase side is maintained in a state where there is no gas (or a state equal to the absence).

  However, when the operation of the refrigerator is stopped for a long period of time, a part of the fluid that is liquid is vaporized due to an increase in the ambient temperature, and bubbles are generated in the dew condensation prevention pipes 62, 63, 64. Sometimes. When many bubbles are generated, the liquid-phase fluid in the dew condensation prevention pipes 62, 63, 64 does not circulate even when the refrigerator is operated, that is, when the circulation pump 61 is started. Therefore, condensation prevention cannot be executed.

  Therefore, in the operation method of the refrigerator of the present embodiment, when the operation of the refrigerator is started, the refrigerator is brought into an operation state in which the piston reciprocates faster than usual. That is, when the piston reciprocates at a higher speed than usual, the high-temperature side evaporator (high-temperature part) 51 is brought into a higher temperature than in normal operation in the heat exchange cycle. For example, in a normal operation, if the high-temperature side evaporator (high-temperature part) 51 is a refrigerator having a temperature of 38 ° C., the high-temperature side evaporator (high-temperature part) until the circulation pump 61 is started as shown in FIG. The piston is driven at a high speed so that 51 becomes 50 ° C. Thereafter, the temperature is gradually lowered when the circulation pump 61 is activated, and normal operation is started when the high-temperature side evaporator (high-temperature part) 51 reaches 38 ° C.

  As described above, when bubbles are generated in the dew condensation prevention pipes 62, 63, 64 at the start of the operation of the refrigerator, the high temperature side evaporator (high temperature part) 51 becomes higher in temperature than in the normal operation. By operating the cooler, bubbles in the dew condensation prevention pipes 62, 63, 64 are pressed by the gas pressure in the high temperature side natural circulation circuit 50, which is a gas phase side pipe. That is, the pressure of the gas in the high-temperature side natural circulation circuit 50 increases the pressure of the fluid on the liquid phase side. Thereby, the gas in the liquid phase is liquefied and the bubbles disappear. Thereafter, when the circulation pump 61 is started, the circulation pump 61 rotates smoothly. By such a method, it is possible to prevent inconvenience at the start of operation.

  FIG. 6 is a flowchart for explaining the startup process of the freezer of the first embodiment. In the startup process of the present embodiment, first, in S1, it is determined whether or not the startup switch of the Stirling refrigeration engine 30 is turned on. In S1, if the cooler start switch is not turned on, the start-up process is not performed, and the process ends. If the start switch of the cooler is turned on in S1, the process proceeds to S2.

  In S2, it is determined whether or not the stop time of the circulation pump 61 is a predetermined time or more. The stop time of the circulation pump 61 is the time measured by the timer from the time when the drive of the circulation pump 61 stops. This stop time data is sequentially stored in a RAM (Random Access Memory) inside the control device 90.

  In S2, if the stop time of the circulation pump 61 does not elapse for a predetermined time or more, the start-up process is not performed and the process is terminated as it is. That is, if the predetermined time or more has not elapsed, the probability of the occurrence of bubbles in the dew condensation prevention pipes 62, 63, 64, etc. is extremely low, so the startup process is not performed. However, instead of measuring the stop time of the circulation pump 61, the condensation prevention pipes 62, 63, 64 are provided with a flow meter for measuring the flow rate of the liquid phase fluid in the condensation prevention pipes 62, 63, 64, and the circulation pump. It may be determined whether to perform the startup process by driving 61, reading the value of the flow meter after a while, and determining whether the circulation pump 61 is driven.

  Next, in S3, the piston driving speed V of the Stirling refrigerating engine 30 is set to an initial value. The piston driving speed V is larger than the driving speed during normal operation. Next, in S4, the piston is operated at a driving speed V that is higher than usual. Accordingly, since the piston is operated at a higher speed than usual, the high temperature side evaporator (high temperature part) 51 of the refrigerator becomes higher in temperature than usual.

  Next, in S5, it is determined whether or not the high temperature side evaporator (high temperature part) 51 has a higher temperature than usual and the operation time in the high temperature state has exceeded a predetermined time. In S5, if the predetermined time has not elapsed, the process returns to S4 and the operation of operating the piston at a higher speed than usual is repeated. Moreover, in S5, when the high temperature side evaporator (high temperature part) 51 is operated for a predetermined time or more at a temperature higher than normal, the process proceeds to S6.

  In S6, the circulation pump 61 is started. The circulation pump 61 is not started until this stage (except when a flow meter is provided) when the Stirling refrigeration engine 30 has been stopped for a predetermined period of time, bubbles are formed in the dew condensation prevention pipes 62, 63, 64. This is because the possibility of occurrence is extremely high, and even if the circulation pump 61 is started, there is a possibility that it will idle.

  Next, it progresses to S7 and it is determined whether the temperature of the high temperature side evaporator (high temperature part) 51 fell. When the liquid phase fluid in the dew condensation prevention pipes 62, 63, 64 starts to circulate, the heat of the high temperature part is transferred to the dew condensation prevention pipes 62, 63, 64, and thus the temperature of the high temperature side evaporator (high temperature part) 51. Decreases. That the temperature of the high temperature portion has decreased means that the liquid phase fluid in the dew condensation prevention pipes 62, 63, 64 has started to circulate due to the start of the circulation pump 61. In S7, if the temperature of the high temperature side evaporator (high temperature part) 51 has not fallen more than the predetermined temperature, the process which stops the circulation pump 61 in S8 is performed. This is because the fact that the temperature of the high temperature side evaporator (high temperature part) 51 does not decrease means that the liquid phase fluid in the dew condensation prevention pipes 62, 63, 64 is not circulated. The determination of whether or not the liquid-phase fluid has been circulated in S7 may be made based on the flow rate if a flow meter is provided.

  Next, in S9, a process of setting the value of V to the initial value × 1.2 is executed. As a result, in step S4, the piston is operated at a high speed at a driving speed of 1.2 V, which is 1.2 times the driving speed V of the previous piston. Thereafter, steps S4 to S7 are repeated. In S7, when the high temperature side evaporator (high temperature part) 51 is lowered by a predetermined temperature, it is determined that the liquid phase fluid in the dew condensation prevention pipes 62, 63, 64 starts to circulate, and in S10, Stirling is performed. Normal operation of the refrigeration engine 30 is started. Thereafter, the startup process is terminated.

  In the above-described embodiment, in order to set the high temperature side evaporator (high temperature part) 51 to a temperature higher than that during normal operation, control is performed to make the piston speed higher (frequency) than during normal operation. However, immediately after the start of the Stirling refrigerating engine 30, the speed (frequency) of the piston is the same as that during normal operation, but the high temperature can also be achieved by controlling the piston stroke to be greater than during normal operation. The side evaporator (high temperature part) 51 can be set to a temperature higher than that during normal operation. Therefore, immediately after the start of the Stirling refrigerating engine 30, even if control for increasing the stroke of the piston is performed compared to during normal operation, the bubbles in the dew condensation prevention pipes 62, 63, 64 are eliminated as described above. Therefore, the circulation pump 61 can be driven.

  In the present specification, the normal operation is a timing at which the operation after the start of the Stirling refrigerating engine 30 is performed, and the circulation pump 61 is stopped or the output of the circulation pump 61 is suppressed. Says timing.

(Embodiment 2)
Next, the refrigerator of the second embodiment will be described. The configuration of the refrigerator of the present embodiment is almost the same as the configuration of the refrigerator of the first embodiment. Therefore, in the present embodiment, only the parts different from the first embodiment will be described.

  The pressure applied to the gas-phase fluid flowing through the high-temperature side natural circulation circuit 50 by changing the operation method of the cooler, that is, the refrigerator, without providing a separate separate heating device as in the refrigerator of the first embodiment. However, as will be described in detail with reference to FIG. 7 in the present embodiment, heating means (for example, a heater) capable of applying heat to the gas-phase fluid flowing in the high-temperature side natural circulation circuit 50 ) 100 may be provided. By operating the heating means 100, it is possible to heat and pressurize the gas phase fluid flowing through the high temperature side natural circulation circuit 50. Thereby, bubbles of the liquid phase fluid staying in the high temperature side forced circulation circuit 60 can be eliminated.

  Further, instead of the heating unit 100 shown in FIG. 7, a pressurizing unit such as a pump capable of applying pressure to the gas phase may be used. Also by this method, bubbles in the liquid phase fluid staying in the high temperature side forced circulation circuit 60 disappear. As a result, it is possible to obtain the same effect as described above.

  Note that the refrigerator of the present embodiment is substantially the same as the refrigerator of the first embodiment. However, in the refrigerator of the present embodiment, as shown in FIG. 7, the heating means 100 capable of heating the gas phase fluid flowing in the high temperature side natural circulation circuit 50 has a high temperature side of the high temperature side natural circulation circuit 50. The point which is provided in the piping through which the fluid flows from the condenser 52 to the high temperature side evaporator 51 is different from the refrigerator of the first embodiment. Further, the control device 90 is configured to be able to heat the gas phase fluid using the heating means 100 based on the information transmitted from the temperature sensor 55 indicating the temperature of the high temperature side evaporator (high temperature part) 51. Has been.

  Hereinafter, the startup process of the freezer of the second embodiment will be described in detail.

  As shown in FIG. 8, in the start-up process of the freezer of the present embodiment, first, in S11, it is determined whether or not the start switch of the cooler has been turned on. If the start switch of the cooler is not turned on in S11, the start-up process is terminated. If the cooler start switch is turned on in S11, the process proceeds to S12, and it is determined whether or not the stop time of the circulation pump is equal to or longer than a predetermined time.

  If the stop time of the circulation pump is not longer than the predetermined time in S12, the startup process is terminated. In S12, if the stop time of the circulation pump is equal to or longer than a predetermined time, the process of S13 is executed. Note that the steps S11 and S12 are the same steps as the steps S1 and S2 of the startup process of the first embodiment.

  Next, in S13, T is a reference value for the temperature to be compared with the temperature of the high temperature side evaporator (high temperature part) 51. Next, in S14, a process for performing heating by the heating means 100 is started. Next, in S15, whether or not the temperature of the high temperature side evaporator (high temperature part) 51 is equal to or higher than the reference value T set in advance, and the time that is the reference value T is longer than a predetermined time (for example, 5 minutes). Is determined.

  In S15, if the temperature of the high temperature side evaporator (high temperature part) 51 is not less than the reference value T and the predetermined time has not elapsed, the step of S14 is continued. In S15, if the temperature of the high temperature side evaporator (high temperature part) 51 is a temperature equal to or higher than the reference value T and a predetermined time or more has elapsed, the process of S16 is executed. In S16, processing for starting the circulation pump 61 is executed. Next, in S <b> 17, it is determined whether or not the temperature of the high temperature side evaporator (high temperature part) 51 has decreased below the temperature of the reference value T. The process of S17 is exactly the same as the process of S7 of the first embodiment.

  In S17, if the temperature of the high temperature side evaporator (high temperature part) 51 is not lower than the temperature of the reference value T, a process of stopping the circulation pump 61 is executed in S18. Thereafter, in S19, the reference value T of the high temperature side evaporator (high temperature part) 51 is set to a new reference value T + 5 that is, for example, 5 degrees higher than the previous reference value T. Thereby, next, in step S14, it is determined whether or not the temperature of the high-temperature side evaporator (high-temperature part) 51 is higher than the reference value with a temperature that is 5 degrees higher than the previous determination process as the reference value. The In this way, steps S14 to S17 are repeated.

  In S17, if the temperature of the high-temperature side evaporator (high-temperature part) 51 decreases by a predetermined temperature or more when the circulation pump 61 is started, the bubbles in the dew condensation prevention pipes 62, 63, 64 disappear. It is determined that the liquid phase fluid in the dew condensation prevention pipes 62, 63, 64 has started to flow. Thereby, in S20, the process which stops the heating by the heating means 100 (heater) is performed. Thereafter, normal operation is started in S21.

  In the present embodiment described above, there is a method of eliminating bubbles in the liquid phase fluid flowing in the high temperature side forced circulation circuit 60 by the heating means 100 for heating the gas phase fluid flowing in the high temperature side natural circulation circuit 50. It is used. However, a pump capable of directly pressurizing the gas phase fluid flowing in the high temperature side natural circulation circuit 50 is provided, and bubbles in the liquid phase fluid flowing in the high temperature side forced circulation circuit 60 are removed by the pressurized gas phase fluid. An extinguishing technique may be used. In this case, the refrigerator has pressure measuring means (for example, a pressure sensor) for detecting the pressure of the gas-phase fluid flowing in the high temperature side natural circulation circuit 50, and the control device 90 is a signal indicating a measurement value by the pressure measuring means. Is preferably configured to control the pressurizing means (e.g., pump) based on the signal.

(Embodiment 3)
Next, the refrigerator of the third embodiment will be described. The configuration of the refrigerator in the present embodiment is almost the same as the configuration of the refrigerator in the first and second embodiments. Therefore, in the present embodiment, only the parts different from the first and second embodiments will be described.

  With reference to FIG. 9, the startup process performed in the control device 90 of the Stirling refrigerating engine 30 according to the third embodiment will be described with reference to a flowchart.

In the start-up process, first, in S21, it is determined whether or not the switch of the Stirling refrigerating engine 30 as the refrigerator is turned on. If the start switch of the cooler is not turned on in S21, the process of S33 is executed. If the start switch of the Stirling refrigerating engine 30 is turned on in S21, the process of S22 is executed. In S22, the operation of the Stirling refrigeration engine 30 is started. Next, in S23, the output of the circulation pump 61 is set to 0 or P _1. Thereafter, in S24, the rotation speed of the cooling fan 110 is set to 0 or V _1.

  Next, in S25, a timer is started. Thereafter, in S26, it is determined whether or not the above-described timer has timed a predetermined time. In S26, if the timer has not passed the predetermined time, the time keeping is continued. If it is determined in S26 that the timer has passed the predetermined time, the process in S28 is executed after the timer is reset in S27.

In S28, the value T ₁ of the wall surface temperature sensor 82 is acquired. Next, in S29, the acquired value T ₂ of the wall temperature sensor 82 again. Thereafter, in S30, the difference between the value T ₁ of the value of T ₂ and the wall surface temperature sensor of the wall surface temperature sensor is calculated. Thereafter, in S30, the difference T ₂ −T ₁ is compared with the predetermined value K. In S30, if the difference T ₂ −T ₁ is not equal to or greater than the predetermined value K, the processes of S29 and S30 are repeated. In S30, if the difference T ₂ −T ₁ is greater than or equal to the predetermined value K, the process of S31 is executed.

In S31, a process of starting the circulation pump 61 or increasing the output of the circulation pump 61 further than P ₁ is executed. Next, in S <b> 32, the control device 90 further increases the rotational speed of the heat dissipation fan 110 than V ₁ .

  Thereafter, in S33, the value H of the wall surface humidity sensor 81 is acquired. Next, in S34, it is determined whether or not the value H of the wall surface humidity sensor 81 is 90% or more. If the value H of the wall surface humidity sensor 81 is 90% or more in S34, the process of S35 is executed. If the value H of the wall surface humidity sensor 81 is smaller than 95% in S34, the process of S35 is executed. Instead, the process of S36 is executed. In S35, the control device 90 decreases the output of the circulation pump 61 or stops the circulation pump 61. Thereafter, control for normal operation of the Stirling refrigeration engine 30 is started in S36.

  In the start-up process of the Stirling refrigerator of the present embodiment, it is determined whether or not a predetermined time has elapsed since the start switch of the Stirling refrigerating engine 30 was turned on in S21 by the processes of S25 to S27. If the predetermined time has elapsed since the start of the Stirling refrigerating engine 30, a process of starting the circulation pump 61 or increasing the output of the circulation pump 61 is executed in S31. Therefore, if the circulation pump 61 is not operated, the temperature of the high-temperature side evaporator (high-temperature part) 51 rises. Therefore, immediately after the operation of the Stirling refrigerating engine 30, the liquid in the dew condensation prevention pipes 62, 63, 64 is increased. The temperature of the phase fluid (refrigerant: water) can be increased. As a result, the temperature of the liquid phase refrigerant (refrigerant: water) in the dew condensation prevention pipe 62 rises, and the pressure of the liquid phase fluid increases. As a result, bubbles remaining in the liquid phase fluid are compressed and disappear. Note that the predetermined time and the output of the circulation pump 61 are stored in the control device 90 in advance as a result of experiments under predetermined conditions.

  Further, in S28 to S30, the initial value of the detected temperature of the wall surface temperature sensor 82 is compared with the detected temperature value of the wall surface temperature sensor 82 after a predetermined time has elapsed, and the detected temperature of the wall surface temperature sensor 82 is determined by the predetermined temperature from the initial temperature. After confirming that the value has decreased, in S31, a process of starting the circulation pump 61 or increasing the output of the circulation pump 61 is performed. Therefore, the operation of the circulation pump 61 is performed after the temperature of the liquid phase fluid (refrigerant: water) in the dew condensation prevention pipe 62 measured by the wall surface temperature sensor 82 is lowered by a predetermined temperature from the start of operation of the Stirling refrigeration engine 30. Or the output of the circulation pump 61 is increased. That is, for example, the cooling space is cooled and the temperature of the wall surface decreases, and accordingly, the temperature of the liquid phase fluid (refrigerant: water) in the dew condensation prevention pipe 62 decreases and remains in the dew condensation prevention pipe 62. A process for starting the circulation pump 61 or increasing the output of the circulation pump 61 is executed after the bubbles to disappear disappear due to condensation. As a result, the generation of noise that occurs when bubbles are rapidly compressed and disappears in the condensation prevention pipes 62, 63, 64 due to the rapid rotation of the circulation pump 61 is suppressed. Note that the predetermined temperature K and the output of the circulating pump 61 are stored in the control device 90 in advance as a result of experiments under predetermined conditions.

  In addition, although the example in which both the above-described processes of S25 to S27 and the above-described processes of S28 to S30 are executed is shown, either one of the processes of S25 to S27 or the processes of S28 to S30 is shown. Even in the case of a refrigerator in which only the condensation is performed, it is possible to suppress the generation of noise caused by the disappearance of bubbles remaining in the dew condensation prevention pipe 62 by the rapid driving of the circulation pump 61.

Further, after the processing of S25 to S30 is completed, the rotational speed of the heat dissipation fan 110 is increased in S32. That is, the output of the rotational speed V ₁ of the radiating fan 110 is increased for the first time in the state where it is estimated that the bubbles remaining in the dew condensation prevention pipes 62, 63, 64 will disappear. In other words, immediately after the Stirling refrigerating engine 30 is started, the rotational speed of the heat radiating fan 110 is smaller than that after the circulation pump 61 is driven. At this time, the heat exchange capability in the high temperature side condenser 52 is low. Therefore, immediately after the start of the Stirling refrigerating engine 30, the temperature of the liquid phase fluid (refrigerant: water) remaining in the dew condensation prevention pipe 62 is higher than after the circulation pump 61 is started. As a result, pressure is applied to the liquid phase fluid in the circulation pipe 61 and the bubbles disappear. As described above, the noise generated by the disappearance of the bubbles remaining in the dew condensation prevention pipe 62 can also be achieved by making the rotational speed of the heat dissipation fan 110 smaller immediately after the start of the Stirling refrigerating engine 30 than immediately after the start of the circulation pump 61. Is suppressed. Note that the rotation speed V ₁ of the heat radiating fan 110 described above is stored in the controller 90 in advance as a result of an experiment under a predetermined condition.

  In S33 to S35, it is determined whether to reduce the output of the circulation pump 61 or to stop the circulation pump 61 depending on whether or not the value of the wall surface humidity sensor 81 is a predetermined value. . That is, since the output of the circulation pump 61 is large, the temperature of the liquid phase fluid in the dew condensation prevention pipes 62, 63, 64 is prevented from becoming lower than the temperature of the surrounding atmosphere. As a result, the temperature of the atmosphere in the vicinity of the dew condensation prevention pipes 62, 63, 64 and the surrounding wall surfaces becomes too low, and the humidity of the atmosphere is prevented from being 100% or more. That is, condensation is prevented from occurring on the wall surface of the refrigerator.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

It is sectional drawing which shows schematic structure of the refrigerator of embodiment. It is a figure which shows the structure of the piping of the refrigerator of embodiment. It is a block diagram for demonstrating a control apparatus. It is a figure for demonstrating the gas-liquid separation apparatus provided around the low temperature part. It is a figure for demonstrating the operating temperature of the circulation pump at the time of driving | running with the operating method of the refrigerator of embodiment. 5 is a flowchart for illustrating a startup process of the refrigerator of the first embodiment. It is a figure for demonstrating the cooler provided with the heating means different from the high temperature part of a cooler. 10 is a flowchart for explaining a startup process according to the second embodiment. 10 is a flowchart for explaining a start-up process according to the third embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Cooling room, 10 Housing, 11, 12, 13 Cooling chamber, 14, 15, 16 Thermal insulation door, 17 Packing, 18 Shelf, 19 Machine room, 20 Duct, 21 Cold-air outlet, 22 Blower fan, 30 Stirling refrigerating engine, 40 Low temperature side circulation circuit, 41 Low temperature side condenser, 42 Low temperature side evaporator, 50 High temperature side natural circulation circuit, 51 High temperature side evaporator, 52 High temperature side condenser, 60 High temperature side forced circulation circuit, 61 Circulation pump, 62, 63, 64 Condensation prevention pipe, 70 Electric heater, 80 Condensation detection unit, 81 Wall surface humidity sensor, 82 Wall surface temperature sensor, 90 Control device, 110 Radiation fan.

Claims (9)

A cooling chamber in which an object to be cooled is stored;
A cooler having a low temperature part for generating cold air for cooling the cooling chamber and a high temperature part for releasing heat generated due to the generation of the cold air;
A liquid phase circulation circuit that is connected to the high temperature section and in which a liquid phase fluid flows;
A liquid phase circulation pump that is provided in the liquid phase circulation circuit and circulates the liquid phase fluid;
Pressurizing means capable of applying pressure to the liquid phase fluid ,
The said pressurizing means is a refrigerator in which the said high temperature part pressurizes by adding heat to the said liquid phase fluid and / or the said gaseous phase fluid . A cooling chamber in which an object to be cooled is stored;
A cooler having a low temperature part for generating cold air for cooling the cooling chamber and a high temperature part for releasing heat generated due to the generation of the cold air;
A liquid phase circulation circuit that is connected to the high temperature section and in which a liquid phase fluid flows;
A liquid phase circulation pump that is provided in the liquid phase circulation circuit and circulates the liquid phase fluid;
A circulation circuit for connecting the high-temperature part and a condenser, and liquefying the vapor phase fluid that is vaporized by receiving heat from the high-temperature part;
Pressurizing means capable of applying pressure to the liquid phase fluid ,
The said pressurization means has a heat source provided separately from the said high temperature part , The refrigerator which is a heating means which can add the heat of the said heat source to the said gaseous-phase fluid . A cooling chamber in which an object to be cooled is stored;
A cooler having a low temperature part for generating cold air for cooling the cooling chamber and a high temperature part for releasing heat generated due to the generation of the cold air;
A liquid phase circulation circuit that is connected to the high temperature section and in which a liquid phase fluid flows;
A liquid phase circulation pump that is provided in the liquid phase circulation circuit and circulates the liquid phase fluid;
A circulation circuit for connecting the high-temperature part and a condenser, and liquefying the vapor phase fluid that is vaporized by receiving heat from the high-temperature part;
Pressurizing means capable of applying pressure to the liquid phase fluid,
The pressurizing means is pressurized by the high-temperature portion applies heat to the liquid-phase fluid and / or the gas phase fluid, cold却庫. A cooling chamber in which an object to be cooled is stored;
A cooler having a low temperature part for generating cold air for cooling the cooling chamber and a high temperature part for releasing heat generated due to the generation of the cold air;
A liquid phase circulation circuit that is connected to the high temperature section and in which a liquid phase fluid flows;
A liquid phase circulation pump that is provided in the liquid phase circulation circuit and circulates the liquid phase fluid;
Pressurizing means capable of applying pressure to the liquid phase fluid,
Said pressurizing means, it said has a heat source provided separately from the high temperature portion, a heating means capable of applying heat of the heat source to the vapor-phase fluid, cold却庫. A cooling chamber in which an object to be cooled is stored;
A cooler having a low temperature part for generating cold air for cooling the cooling chamber and a high temperature part for releasing heat generated due to the generation of the cold air;
A liquid phase circulation circuit that is connected to the high temperature section and in which a liquid phase fluid flows;
A liquid phase circulation pump that is provided in the liquid phase circulation circuit and circulates the liquid phase fluid;
A cooling circuit comprising a circulation circuit that connects the high-temperature part and a condenser and liquefies a vapor phase fluid that is vaporized by receiving heat from the high-temperature part,
By applying a pressure higher than the pressure applied during normal operation to the gas phase fluid from the start of operation of the refrigerator until the liquid phase fluid is properly circulated by the liquid phase circulation pump, A method of operating a refrigerator in which pressure is applied to a liquid phase fluid. A cooling chamber in which an object to be cooled is stored;
A cooler having a low temperature part for generating cold air for cooling the cooling chamber and a high temperature part for releasing heat generated due to the generation of the cold air;
A liquid phase circulation circuit that is connected to the high temperature section and in which a liquid phase fluid flows;
A liquid phase circulation pump that is provided in the liquid phase circulation circuit and circulates the liquid phase fluid;
A circulation circuit for connecting the high-temperature part and a condenser, and liquefying the vapor phase fluid that is vaporized by receiving heat from the high-temperature part ;
A control device for controlling the cooler,
The control device has a predetermined temperature higher than that during normal operation when the high-temperature part is in the cooler until the liquid-phase fluid is properly circulated by the liquid-phase circulation pump from the start of operation of the refrigerator. A refrigerator that executes control for operating the piston of the cooler at a high speed or control for increasing a stroke of the piston of the cooler so as to reach a temperature. A cooling chamber in which an object to be cooled is stored;
A cooler having a low temperature part for generating cold air for cooling the cooling chamber and a high temperature part for releasing heat generated due to the generation of the cold air;
A liquid phase circulation circuit that is connected to the high temperature section and in which a liquid phase fluid flows;
A liquid phase circulation pump that is provided in the liquid phase circulation circuit and circulates the liquid phase fluid;
A controller for controlling the cooler and the liquid phase circulation pump,
The said control apparatus is a refrigerator which starts the said liquid phase circulation pump or increases the output of the said liquid phase circulation pump on condition that the predetermined time passed after starting the driving | operation of the said cooler. A cooling chamber in which an object to be cooled is stored;
A cooler having a low temperature part for generating cold air for cooling the cooling chamber and a high temperature part for releasing heat generated due to the generation of the cold air;
A dew condensation prevention pipe that is provided along the inner surface of the housing and is connected to the high temperature part and through which a liquid fluid flows.
A liquid phase circulation pump that is provided in a liquid phase circulation circuit including the condensation prevention pipe and circulates the liquid phase fluid;
A control device for controlling the cooler and the liquid phase circulation pump;
A temperature sensor for measuring the temperature of the surface of the housing or the liquid phase circulation pipe;
The said control apparatus is a refrigerator which starts the said liquid phase circulation pump or increases the output of the said liquid phase circulation pump on condition that the detection temperature of the said temperature sensor fell. A cooling chamber in which an object to be cooled is stored;
A cooler having a low temperature part for generating cold air for cooling the cooling chamber and a high temperature part for releasing heat generated due to the generation of the cold air;
A liquid phase circulation circuit that is connected to the high temperature section and in which a liquid phase fluid flows;
A liquid phase circulation pump that is provided in the liquid phase circulation circuit and circulates the liquid phase fluid;
A radiator for lowering the temperature of the high temperature part,
A heat dissipating fan provided in the vicinity of the radiator,
A controller for controlling the cooler, the liquid phase circulation pump, and the heat dissipating fan;
The controller, after starting the cooler, before starting the liquid phase circulation pump, stop the heat dissipation fan, or compared after starting the liquid phase circulation pump, A refrigerator that drives the heat dissipation fan with a smaller output.

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