JP6282255B2 - refrigerator - Google Patents

Description

  The present invention relates to a refrigerator.

  As a background art in this technical field, there is JP 2009-174767 A (Patent Document 1).

  In Patent Document 1, a compressor and a condenser constituting a refrigeration cycle are provided in a heat insulating box body in which a storage chamber is formed, and a dew condensation prevention pipe disposed at the opening peripheral edge of the storage chamber is a pipe of the refrigeration cycle. Is provided with a switching means that can be switched between a heating mode for circulating the refrigerant through the dew condensation prevention pipe and a normal mode for bypassing the dew condensation prevention pipe, and controls the operation of the compressor and the operation of the switching means. The apparatus is provided with a refrigerator, and a dew condensation prevention pipe is connected between the compressor and the condenser, and the control device performs on / off control of the operation of the compressor and controls the switching means to thereby compress the compressor. A technique is disclosed in which the heating mode is executed in a part of the operation on period of the machine and the normal mode is executed in other periods (Patent Document 1, FIGS. 1 to 3 and the like).

JP 2009-174767 A

  However, in the technique described in Patent Document 1, consideration is not sufficiently given to the structure and control, and the energy saving performance cannot be sufficiently increased.

  This invention is made | formed in view of the said subject, and it aims at improving the energy-saving performance of the refrigerator provided with the heating means which heats the opening peripheral part (partition part) of a storage chamber.

In order to solve the above problems, for example, the configuration described in the claims is adopted. The present application includes a plurality of means for solving the above-mentioned problems. To give an example, a storage chamber provided in a heat insulating box and having an opening, a partition section for partitioning the opening, and contacting the partition section. And a heating means for heating the partition portion, wherein the depth dimension of the gap between the doors is 3 of the width dimension of the gap between the plurality of doors. More than double, the width dimension of the gap between the doors is 10 mm or less, a detection means for detecting the temperature and humidity of the ambient air of the refrigerator, and a heating amount control means for controlling the heating amount of the heating means The heating means is a heat radiating pipe provided between the compressor and the decompression means, and the time during which the temperature of the partitioning portion is not higher than the dew point temperature of the ambient air is not more than the dew point temperature. The length of the During an average value Ri executable der a mode for controlling the heating amount control means to have a dew point temperature or less of the ambient air, when the humidity of the ambient air detected by said detecting means is a predetermined value greater than the refrigerant which the compressor is discharged from the compressor when it is operated, characterized that you control the heating amount control means in a state flowing in the vacuum means through the heat dissipating means.

  ADVANTAGE OF THE INVENTION According to this invention, the energy saving performance of the refrigerator provided with the heating means which heats the opening peripheral part (partition part) of a store room can be made high enough.

The front external view of the refrigerator which concerns on embodiment of this invention. XX sectional drawing of FIG. 1 showing the structure in the refrigerator compartment which concerns on embodiment of this invention. The figure showing the structure of the refrigerating cycle of the refrigerator which concerns on embodiment of this invention. The figure showing the arrangement | positioning position of the heat radiating pipe of the refrigerator which concerns on embodiment of this invention. The principal part expanded sectional view showing the structure of the horizontal partition part vicinity of the refrigerator which concerns on embodiment of this invention. The flowchart showing control of the refrigerator which concerns on embodiment of this invention. The time chart showing the control and temperature change of the refrigerator which concerns on embodiment of this invention. The schematic diagram showing the water vapor | steam movement between the door gaps of the refrigerator which concerns on embodiment of this invention. The figure showing the temperature change of the partition part of the refrigerator which concerns on embodiment of this invention.

  An embodiment of a refrigerator according to the present invention will be described with reference to FIGS.

  FIG. 1 is a front outline view of the refrigerator of the present embodiment. FIG. 2 is a cross-sectional view taken along the line XX in FIG. 1 showing the configuration inside the refrigerator. FIG. 3 is a diagram illustrating the configuration of the refrigeration cycle of the refrigerator of the present embodiment. FIG. 4 is a diagram illustrating the disposition positions of the heat radiating pipes in the refrigerator of the present embodiment. FIG. 5 is an enlarged view of the vicinity of the region A shown in FIG. 2 and is an enlarged cross-sectional view of the main part showing the configuration in the vicinity of the horizontal partition portion of the refrigerator according to the embodiment of the present invention.

  As shown in FIG. 1, the refrigerator 1 of the present embodiment includes a refrigerator compartment 2, an ice making compartment 3, an upper freezer compartment 4, a lower freezer compartment 5, and a vegetable compartment 6 from above. The ice making chamber 3 and the upper freezing chamber 4 are provided side by side between the refrigerator compartment 2 and the lower freezing chamber 5. The refrigerated room 2 and the vegetable room 6 are storage rooms in a refrigerated temperature zone of approximately 3 to 5 ° C. Further, the ice making room 3, the upper freezer room 4, and the lower freezer room 5 are storage rooms in a freezing temperature zone of approximately −18 ° C.

  The refrigerating room 2 is provided with double door-type refrigerating room doors 2a and 2b that are divided into left and right on the front side. The ice making room 3, the upper freezing room 4, the lower freezing room 5, and the vegetable room 6 include a drawer type ice making room door 3a, an upper freezing room door 4a, a lower freezing room door 5a, and a vegetable room door 6a, respectively. Further, a seal member 70 (see FIG. 5) is provided on the surface of each door on the storage chamber side along the outer edge of each door. When each door is closed, the outside air enters and stores the storage chamber. Suppresses cold air leakage from the room.

  Moreover, the refrigerator 1 of this embodiment has a door sensor (not shown) that detects the open / closed state of the door provided in each storage room, and a state in which each door is determined to be open for a predetermined time, for example, An alarm (not shown) for notifying the user when the operation is continued for one minute or more, a temperature setting device for setting the temperature of the refrigerator compartment 2, the temperature of the upper freezer compartment 4 and the lower freezer compartment 5, etc. Not shown).

  As shown in FIG. 2, the outside of the refrigerator 1 and the inside of the refrigerator 1 according to this embodiment are formed by filling a foam insulation (foamed polyurethane) between the outer box 1a and the inner box 1b. 10 separated by 10. Moreover, the refrigerator 1 of this embodiment is equipped with a plurality of vacuum heat insulating materials 25.

  In the refrigerator 1 of this embodiment, the refrigerator compartment 2, the upper freezer compartment 4, and the ice making chamber 3 (see FIG. 1, the ice making chamber 3 is not shown in FIG. 2) are insulated by the upper heat insulating partition wall 51. The lower freezing compartment 5 and the vegetable compartment 6 are insulated from each other by the lower heat insulating partition wall 52. Further, as indicated by a broken line in FIG. 1, a horizontal partition 53 is provided in the upper part of the lower freezer compartment 5. The horizontal partition 53 partitions the ice making chamber 3 and the upper freezing chamber 4 and the lower freezing chamber 5 in the vertical direction. In addition, a vertical partition 54 that partitions the ice making chamber 3 and the upper freezing chamber 4 in the left-right direction is provided above the horizontal partition 53.

  The horizontal partition 53 receives the seal member 70 provided on the storage room side surface of the lower freezer compartment door 5a together with the front surface of the lower heat insulating partition wall 52 and the front surfaces of the left and right side walls, and receives the lower freezer compartment 5 and the lower freezer compartment door 5a. The movement of gas between the two. Further, the seal member 70 provided on the surface of the ice making room door 3 a and the upper freezing room door 4 a on the storage room side is in contact with the horizontal partition 53, the vertical partition 54, the upper heat insulating partition wall 51, and the front surfaces of the left and right side walls of the refrigerator 1. This suppresses the movement of gas between each storage chamber and each door (detailed structure will be described later).

  Since the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5 are all freezing temperature zones, the horizontal partition 53 and the vertical partition 54 are at least on the front side of the refrigerator in order to receive the seal member of each door. What is necessary (see FIG. 2). That is, there may be a movement of gas between the storage chambers in the freezing temperature zone, and there may be a case where the heat insulation section is not provided. On the other hand, in the case where the upper freezer compartment 4 is a temperature switching chamber, it is necessary to make a heat insulating compartment, and therefore the horizontal partition 53 and the vertical partition 54 extend from the front side of the refrigerator 1 to the rear wall.

  The refrigerator 1 of the present embodiment includes a plurality of door pockets 32 on the storage room side of the refrigerator compartment doors 2a and 2b (see FIG. 2). Further, the refrigerator compartment 2 is provided with a plurality of shelves 90. The refrigerator compartment 2 is partitioned into a plurality of storage spaces in the vertical direction by shelves 90.

  As shown in FIG. 2, the upper freezer compartment 4, the lower freezer compartment 5, and the vegetable compartment 6 are storage containers 3b, 4b, 5b, 6b that move in the front-rear direction together with the doors provided in front of the respective storage compartments. It has. The ice making room door 3a, the upper freezer compartment door 4a, the lower freezer compartment door 5a, and the vegetable compartment door 6a are each pulled out to the front side by placing a hand on a handle portion (not shown) so that the storage containers 3b, 4b, 5b, 6b It can be pulled out.

  As shown in FIG.2 and FIG.3, the refrigerator 1 of this embodiment is provided with the evaporator 7 as a cooling means. The evaporator 7 (for example, a fin tube type heat exchanger) is provided in an evaporator storage chamber 8 provided substantially at the back of the lower freezing chamber 5. In addition, an internal fan 9 (propeller fan as an example) is provided as a blowing means in the evaporator storage chamber 8 and above the evaporator 7.

  Air that has been cooled by exchanging heat with the evaporator 7 (hereinafter, low-temperature air that has been heat-exchanged by the evaporator 7 is referred to as “cold air”) is cooled by a refrigerator 9 in the refrigerator compartment air duct 11 and the vegetable compartment air duct. (Not shown), it is sent to the respective storage rooms of the refrigerator compartment 2, the vegetable compartment 6, the ice making chamber 3, the upper freezer compartment 4, and the lower freezer compartment 5 through the upper freezer compartment blower duct 16. The ventilation to each storage room is performed by a refrigerator compartment damper 80 for controlling the amount of air sent to the refrigerator compartment 2, a vegetable compartment damper (not shown) for controlling the amount of air sent to the vegetable compartment 6, and a freezing temperature zone compartment (ice making). It is controlled by a freezer damper 81 that controls the amount of air blown into the chamber 3, the upper freezer 4 and the lower freezer 5).

  When ventilation to the refrigerator compartment 2 is performed with the refrigerator compartment damper 80 in the open state, the cold air flows into the refrigerator compartment 2 from the outlets 2 c provided in multiple stages via the refrigerator compartment air duct 11. The cold air that has cooled the refrigerator compartment 2 passes through a refrigerator compartment return duct (not shown) provided on the side of the evaporator storage chamber 8 from a refrigerator compartment return port (not shown) provided in the lower portion of the refrigerator compartment 2. Return to the lower part of the evaporator storage chamber 8.

  When the vegetable room damper is opened and air is blown to the vegetable room 6, the cold air flows into the vegetable room 6 from the vegetable room outlet (not shown) through the vegetable room air duct (not shown). The cool air that has cooled the vegetable compartment 6 passes from the vegetable compartment return duct inlet 18b provided in front of the lower part of the lower heat insulating partition wall 52 through the vegetable compartment return duct 18 and from the vegetable compartment return duct outlet 18a to the evaporator storage chamber 8. Return to the bottom.

  As shown in FIG. 2, the refrigerator 1 of the present embodiment includes a partition member 13 that partitions each storage chamber and the evaporator storage chamber 8 in front of the evaporator storage chamber 8. The partition member 13 is formed with blowout ports 3c, 4c, and 5c, and when the freezer damper 81 is in an open state, the cold air is blown into an ice making fan blow duct, an upper freezer blower duct 16, and a lower freezer blower (not shown). It flows into the upper freezer compartment 4, the lower freezer compartment 5, and the ice making chamber 3 through the ducts 12 through the outlets 3 c, 4 c, and 5 c. The partition member 13 is provided with a freezer return port 17 at a position in the lower part of the lower freezer compartment 5, and cool air that has cooled the freezing temperature zone (the ice making room 3, the upper freezer room 4, the lower freezer room 5). Flows into the evaporator storage chamber 8 via the freezer return port 17. The freezer compartment return port 17 has a width dimension substantially equal to the width of the evaporator 7.

  Generally, cold air having a low temperature with respect to the ambient temperature forms a downward flow from the upper side to the lower side. Therefore, by supplying more cold air to the upper side of the storage chamber, the storage chamber can be favorably cooled by the action of the downward flow. In this embodiment, the freezer compartment damper 81 is provided. However, by installing the freezer damper 81 above the internal fan 9, the air from the internal fan 9 can be smoothly blown to the ice making chamber 3 and the upper freezer compartment 4. Consideration is taken. Further, if the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5 are configured to communicate with each other, the cooling effect by the downflow can be enhanced.

  As shown in FIG. 2, a defrost heater 22 is provided below the evaporator storage chamber 8. The frost that has grown on the wall of the evaporator 7 and the surrounding evaporator storage chamber 8 is melted by energizing and heating the defrost heater 22. The defrost water generated by melting of the frost flows into the eaves 23 provided at the lower part of the evaporator storage chamber 8 shown in FIG. 2, and is then disposed in the machine chamber 19 through the drain pipe 27. 21 is reached. The defrost water in the evaporating dish 21 evaporates due to heat generated by the compressor 24 and the condenser 61 (not shown in FIG. 2) disposed in the machine room 19.

  Next, the refrigeration cycle in the present embodiment will be described with reference to FIGS. 3 to 5 and FIG. 2 as appropriate. As shown in FIG. 3, the refrigerator 1 according to the present embodiment includes a compressor 24 that compresses a refrigerant, a heat dissipating unit 60 that dissipates the refrigerant sent from the compressor 24, and decompresses the refrigerant sent from the heat dissipating unit 60. A pressure reducing means, a capillary tube 43, and an evaporator 7 as a cooling means for cooling the air sent from the capillary tube 43 by evaporating, and these are sequentially connected by a pipe through which the refrigerant flows. It constitutes the refrigeration cycle.

  The compressor 24 is arrange | positioned in the machine room 19 provided in the lower back of the refrigerator 1, as shown in FIG.

  As shown in FIG. 3, the heat radiating means 60 includes a condenser 61 (for example, a finned tube heat exchanger) and heat radiating pipes 62 and 64 disposed in the machine room 19 (see FIG. 2). An outside fan 26 is disposed in the machine room 19 (not shown in FIG. 2), and the heat from the condenser 61 can be promoted by driving the outside fan 26. It has become.

  The heat radiating pipe 62 (illustrated by a dotted line in FIG. 4) is arranged between the outer box 1a and the inner box 1b on both side surfaces, the back surface, and the ceiling surface of the heat insulating box 10 so as to be in contact with the surface of the outer box 1a. It is installed. The outer box 1a is made of a steel plate, and heat is radiated well from the outer surface of the outer box 1a to the outside air.

  Further, the heat radiating pipe 64 is disposed in front of the front edge surface as indicated by a broken line in FIG. 4 so as to heat the front edge surface of the opening of the heat insulation box 10. The heat insulation partition wall 51, the lower heat insulation partition wall 52, the horizontal partition part 53, and the vertical partition part 54 can be heated. Since these partition walls (partition portions) are in low temperature because they are in contact with the storage chambers, the front portion serves as an opening edge of each storage chamber, so that the partition walls (partition portions) are likely to come into contact with the outside air and easily cause condensation.

  A three-way valve 65 as a heat dissipation performance control means is disposed in the machine room 19 (not shown in FIGS. 2 and 4). The outlet pipe of the heat radiating pipe 62 enters the machine room 19 (see FIG. 4) and is connected to the inlet pipe of the three-way valve 65. The three-way valve 65 is formed at one inlet (65a) and two outlets (65b, 65c). A state in which the refrigerant flowing from the inlet 65a flows to the outlet 65b (hereinafter referred to as "state A"), and the inlet 65a This is a motor-operated valve capable of switching and controlling the state (hereinafter referred to as “state B”) of flowing the refrigerant flowing into the outlet 65c. The outlet pipe of the three-way valve 65 is connected to the inlet pipe of the heat radiating pipe 64, and the outlet pipe of the three-way valve 65 is connected to the inlet pipe of the bypass pipe 63 (see FIG. 3).

  A check valve 67 is disposed at the outlet pipe of the heat radiating pipe 64 (see FIG. 3). The outlet pipe of the heat radiating pipe 64 and the outlet pipe of the bypass pipe 63 are connected to and joined with a joining pipe (not shown) in the machine room. A dryer 41 is disposed at the outlet pipe of the junction pipe, and the outlet pipe of the dryer is connected to an inlet pipe of a two-way valve 66 as a refrigerant flow rate adjusting means. The dryer 41 and the two-way valve 66 are installed in the machine room 19. The outlet pipe of the two-way valve 66 is connected to the capillary tube 43. Further, the dryer 41 is for drying and absorbing moisture in the refrigerant, and prevents the inside of the tube from being frozen and clogged, so that the refrigerant does not circulate.

  The pipe 68a, which is a part of the pipe 68 from the evaporator 7 toward the compressor 24, is close to or in contact with the capillary tube 43, and the heat in the capillary tube 43 moves to the refrigerant in the pipe 68a. (See FIG. 3). Further, as shown in FIG. 4, the heat-dissipating pipe 64 for preventing condensation is disposed mainly on the front opening edge of the storage room in the freezing temperature zone where the temperature difference becomes large.

  FIG. 5 is an enlarged view of the vicinity of the region A shown in FIG. As shown in FIG. 5, the horizontal partition 53 is provided with a heat conducting member 53a (as an example, a metal plate such as a steel plate) on the front surface, and a heat insulating material 53b (as an example, styrofoam) inside the horizontal partition 53. , Foam insulation such as urethane) is disposed. The heat radiating pipe 64 is disposed between the heat insulating material 53b and the steel plate 53a, and is in close contact with the steel plate 53a via a heat conductive buffer material (not shown). A partition temperature sensor 38 is disposed inside the horizontal partition 53 so as to be in close contact with the steel plate 53a. In addition, a seal member 70 in which a magnet is mounted is provided on the surface facing the horizontal partition 53 inside the upper freezer compartment door 4a and the lower freezer compartment door 5a. When each door is closed, the intrusion of outside air into the storage chamber and the cold air leakage from the storage chamber are suppressed by the adsorption action of the magnet. In the refrigerator 1 of the present embodiment, the vertical dimension (gap width) L1 between the upper freezer compartment door 4a and the lower freezer compartment door 5a is 10 mm or less, and the refrigerator 1 of the present embodiment is L1 = 7 mm. Moreover, the depth dimension (gap depth) L2 from the steel plate 53a surface which is the front surface of the horizontal partition part 53 to the freezer compartment door front edge is set to three times or more of L1, and the refrigerator 1 of this embodiment is L2 = 40 mm. In addition, although the structure of the horizontal partition part 53 vicinity was demonstrated here, it is the same structure also about the vertical partition part 54, the upper side heat insulation partition wall 51, and the lower side heat insulation partition wall 52, and the clearance gap width L1 between doors. Is 10 mm or less, and the gap depth L2 between the doors is 30 mm or more, which is three times or more of L1.

  As shown in FIG. 2, the refrigerator 1 includes an evaporator temperature sensor 35 attached to the evaporator 7, an refrigerator temperature sensor 33 in the refrigerator room 2, and a freezer compartment temperature sensor in the lower freezer room 5. 34, respectively, and detects the temperature of the evaporator 7, the temperature of the refrigerator compartment 2, and the temperature of the lower freezer compartment 5, respectively.

  Furthermore, the refrigerator 1 is a heat insulating box provided with an outside air temperature sensor 36, an outside air humidity sensor 37, and a heat radiating pipe 64, which are detection means for detecting the temperature and humidity (outside air temperature, outside air humidity) of the surrounding environment. The partition part temperature sensor 38 which detects ten front opening edge temperatures is provided. The vegetable compartment 6 is also provided with a vegetable compartment temperature sensor 33a. The cold storage room temperature sensor 33, the vegetable room temperature sensor 33a, and the freezer room temperature sensor 34 are installed in a place where the cold air blown into each storage room is not directly applied to improve detection accuracy.

  As a control device, a control board 31 on which a CPU, a memory such as a ROM and a RAM, an interface circuit, and the like are mounted is disposed on the upper surface of the ceiling wall of the refrigerator 1 (see FIG. 2). The control board 31 includes the outside air temperature sensor 36, the outside air humidity sensor 37, the evaporator temperature sensor 35, the refrigerator compartment temperature sensor 33, the vegetable compartment temperature sensor 33a, the freezer compartment temperature sensor 34, the partition temperature sensor 38, and each storage compartment. It connects with the door sensor which detects the opening-and-closing state of a door, respectively, the temperature setting device provided in the refrigerator compartment door 2a, the power saving mode setting device, etc. Each program (not shown) for individually operating the compressor 24 ON / OFF, the three-way valve 65, the two-way valve 66, the refrigerator compartment damper 80, the vegetable compartment damper, and the freezer compartment damper 81 according to a program previously installed in the ROM. Control of the actuator, ON / OFF control and rotation speed control of the internal fan 9 and the external fan 26, control of ON / OFF of an alarm for notifying the door open state described above, and the like are performed. The temperature setting device and the power saving mode setting device can use known operation means such as a mechanical switch, an electric switch, and a capacitance switch that can be manually operated and changed by the user.

  Next, control of the refrigerator 1 of this embodiment is demonstrated, referring FIG.6 and FIG.7. FIG. 6 is a control flowchart showing the control during the cooling operation of the refrigerator 1 of the present embodiment, and FIG. 7 shows the change in the surface temperature of the horizontal partitioning portion and the control state when the three-way valve switching control of the refrigerator 1 of the present embodiment is performed. It is a time chart showing. The control is performed by the control device, that is, the CPU of the control board 31 (see FIG. 2) executing a program stored in the ROM.

  As shown in FIG. 6, the refrigerator 1 starts the cooling operation by turning on the power supply and starts the cooling operation (“start” in FIG. 6). The cooling operation is an operation that drives the compressor 24 and heats the cold air exchanged by the evaporator 7 to drive the internal fan 9 to the respective storage chambers.

  At this time, as an initial state, the three-way valve 65 is in the above-described state A (the state in which the refrigerant flowing from the inlet 65a flows from the outlet 65b to the heat radiating pipe 64 (see FIG. 3)). Subsequently, based on the detection information of the outside air temperature sensor 36 and the outside air humidity sensor 37, it is determined whether or not the condition of the mode i of the three-way valve switching control is established (step S101). In the refrigerator 1 of the present embodiment, the condition of the mode i of the three-way valve switching control is established when “the outside air temperature is 35 ° C. or less”, “the outside air humidity is 80% or less”, and “the power saving mode is OFF”. In addition, ON / OFF of power saving mode is set by the power saving mode setting device provided in the refrigerator compartment door 2a. When the condition of the mode i of the three-way valve switching control is not satisfied (No), it is subsequently determined whether or not the condition of the mode ii of the three-way valve switching control is satisfied (step S102). In the refrigerator 1 of the present embodiment, the condition of the mode ii of the three-way valve switching control is established when “the outside air temperature is 40 ° C. or less”, “the outside air humidity is 85% or less”, and “the power saving mode is ON”.

  Mode i is a control mode in which the time average temperature of the partition surface during stable operation is equal to or higher than the dew point temperature, and mode ii is a control where the time average temperature of the partition surface during stable operation is equal to or lower than the dew point temperature. Mode, which can be set by the user with the power saving mode setting device. Details will be described later.

  If the condition for mode ii of the three-way valve switching control is not satisfied (No), it is subsequently determined whether or not the condition for compressor OFF is satisfied (step S103). In the refrigerator 1 of the present embodiment, the compressor OFF condition is established when the temperatures detected by the freezer temperature sensor 34, the refrigerator temperature sensor 33, and the vegetable room temperature sensor 33a are each equal to or lower than a predetermined temperature. Note that the temperature at which the compressor-off condition is established is calculated based on the setting of the temperature setting device provided in the refrigerator compartment door 2a. The refrigerator 1 of the present embodiment is capable of selecting “strong (lower storage room temperature)”, “medium (standard)”, and “weak (higher storage room temperature)” by the temperature setting device. The compressor OFF condition when “medium” is set is “freezer compartment temperature −21 ° C. or lower, refrigerator compartment temperature 5 ° C. or lower, vegetable compartment temperature 5 ° C. or lower”.

  When the condition for compressor OFF is not satisfied (No), the process returns to the determination of step S101 again. When the condition for compressor OFF is satisfied (Yes), the three-way valve 65 is set to state A (step S104). After the duration time of state A reaches t1 (step S105), the two-way valve 66 is closed (step S106), and the compressor is turned off (step S107). Thus, by closing the two-way valve 66 when the compressor is stopped, it is possible to prevent the high-temperature and high-pressure refrigerant in the heat radiation means 60 from flowing into the evaporator 7 via the capillary tube 43 and becoming a heat load. Therefore, energy saving performance becomes high. In the refrigerator 1 of the present embodiment, t1 = 15 minutes.

  Subsequently, it is determined whether or not the compressor ON condition is satisfied (step S108). In the refrigerator 1 of the present embodiment, the compressor ON condition is established when the temperature detected by the freezer temperature sensor 34 rises to a predetermined temperature. For example, the compressor ON condition when the temperature setting device is set to “medium” is “freezer temperature −19 ° C. or higher”. In addition, although the refrigerator 1 of this embodiment has determined the conditions of compressor ON by the freezer compartment temperature, this is because the refrigerator 1 of this embodiment has the refrigerator compartment 2 and the vegetable compartment 6 also during compressor OFF. This is because cooling can be performed. Specifically, during the compressor OFF, the refrigerator compartment 2 and the vegetable compartment 6 have the freezer damper 81 closed, the refrigerator compartment damper 80 and the vegetable compartment damper open, and the internal blower 9 is operated, and the cooler It cools with the cold heat of the frost adhering to 7. In the case where only one of the refrigerator compartment 2 or the vegetable compartment 6 is cooled by closing one of the refrigerator compartment damper 80 or the vegetable compartment damper based on the temperature detected by the refrigerator compartment temperature sensor 33 or the vegetable compartment temperature sensor 33a. There is also.

  If the compressor ON condition is satisfied (Yes), then the two-way valve 66 is opened (step S109), and the compressor is operated at a higher speed than in the normal cooling operation to restart the cooling operation ( Step t110) After t2 has elapsed (in the refrigerator 1 of the present embodiment, t2 = 30 seconds) (step S111), the compressor rotational speed is reduced to the rotational speed during normal cooling operation (step S112). The compressor speed controlled in steps S110 and S112 is set based on the temperature detected by the outside air temperature sensor 36. For example, when the outside air temperature is 30 ° C., the compressor is set to 2500 r in step S110. / Min, and the rotational speed is reduced to 1600 r / min in step S112.

  Next, the case where the condition for mode i or the condition for mode ii of the three-way valve switching control is satisfied in step S101 or step S102 will be described.

  When the condition of mode i is satisfied in step S101 (Yes), it is subsequently determined whether a switching condition for switching the three-way valve in mode i from state A to state B is satisfied (step S201). In the refrigerator 1 of the present embodiment, the condition for switching from the state A to the state B is established by “the duration of the state A has elapsed t3” or “the elapsed time since the compressor has been started since the start time t3 has elapsed”. . Note that t3 is calculated based on the temperature and humidity detected by the outside air temperature sensor 36 and the outside air humidity sensor 37. In step S201, when the switching condition from state A to state B is not satisfied (No), the process proceeds to the determination of step S202. When step S201 is satisfied (Yes), the three-way valve is switched to state B. (Step S204), the process proceeds to step S202.

  In step S202, it is determined whether or not a switching condition for switching the three-way valve in mode i from state B to state A is satisfied. The refrigerator 1 according to the present embodiment has any one of “continuation time of state B t4”, “door opening operation (detection by door sensor)”, or “partition temperature sensor 38 detection temperature reaches lower limit temperature Tmin1”. When such a condition is satisfied, the switching condition from the state B to the state A is satisfied. Note that t4 is calculated based on the temperature and humidity detected by the outside air temperature sensor 36 and the outside air humidity sensor 37. The lower the temperature and humidity, the longer the ratio of t4 to t3. For example, in the refrigerator 1 of the present embodiment, when the outside air temperature is 30 ° C. and the outside air humidity is 70%, t3 = 20 minutes and t4 = 10 minutes. When the outside air temperature is 15 ° C. and the outside air humidity is 55%, t3 = 20 minutes. t4 = 20 minutes. Tmin1 is set to Tmin1 = Tdew−5 [° C.] with respect to the dew point temperature Tdew calculated based on the temperature and humidity detected by the outside air temperature sensor 36 and the outside air humidity sensor 37.

  In step S202, when the switching condition from state B to state A is not satisfied (No), the process proceeds to the determination of step S203, and when step S202 is satisfied (Yes), the three-way valve is changed to state A in step S205. After switching to step S203, the process proceeds to step S203.

  In step S203, it is determined whether or not the compressor OFF condition is satisfied. Note that the compressor-off condition in step S203 is the same as that in step S103. When the compressor OFF condition is satisfied in step S203 (Yes), the process proceeds to step S104, and when step S203 is not satisfied (No), the process returns to the determination in step S201.

  When the condition of mode ii is satisfied in step S102 (Yes), it is subsequently determined whether or not the condition for switching from state A to state B in mode ii is satisfied (step S301). In the refrigerator 1 according to the present embodiment, the condition for switching from the state A to the state B is satisfied by “the continuation time of the state A is t5” or “the elapsed time after the compressor is started from the stop state is t5”. . Note that t5 is calculated based on the temperature and humidity detected by the outside air temperature sensor 36 and the outside air humidity sensor 37. In step S301, if the switching condition for switching the three-way valve from state A to state B is not satisfied (No), then the process proceeds to step S302, and if step S301 is satisfied (Yes), the three-way valve is in the state. After switching to B (step S304), the process proceeds to the determination in step S302.

  In step S302, it is determined whether or not a switching condition for switching the three-way valve in mode ii from state B to state A is satisfied. The refrigerator 1 of the present embodiment is any one of “the duration B of state B has elapsed t6”, “the door opening operation (detection by the door sensor)”, or “the temperature detected by the partition temperature sensor 38 reaches the lower limit temperature Tmin2”. The condition for switching from state B to state A is satisfied when the above condition is satisfied. Note that t6 is calculated based on the temperature and humidity detected by the outside air temperature sensor 36 and the outside air humidity sensor 37. The lower the temperature and humidity, the longer the ratio of t6 to t5. For example, in the refrigerator 1 of the present embodiment, when the outside air temperature is 30 ° C. and the outside air humidity is 70%, t5 = 15 minutes and t6 = 20 minutes, and when the outside air temperature is 15 ° C. and the outside air humidity is 55%, t5 = 20 minutes. t6 = 40 minutes. Tmin2 is set to Tmin2 = Tdew−8 [° C.] with respect to the dew point temperature Tdew calculated based on the temperature and humidity detected by the outside air temperature sensor 36 and the outside air humidity sensor 37.

  If the switching condition from state B to state A is not satisfied in step S302 (No), then the process proceeds to step S303, and if step S302 is satisfied (Yes), the three-way valve is switched to state A. (Step S305), the process proceeds to step S303.

  In step S303, it is determined whether or not the compressor OFF condition is satisfied. Note that the compressor-off condition in step S303 is the same as that in step S103. If the compressor OFF condition is satisfied in step S303 (Yes), the process proceeds to step S104. If step S303 is not satisfied (No), the process returns to the determination in step S301.

  Next, when the refrigerator 1 according to the present embodiment is set in the power saving mode and installed in an environment with a temperature of 30 ° C. and a relative humidity of 70%, and is in a stable operation state (details conform to JIS C9801: 2006). The temperature change of the surface of the horizontal partition 53 (the surface of the steel plate 53a) and the control state of the three-way valve 65, the two-way valve 66, and the compressor 24 will be described with reference to FIG. The stable operation state refers to a state in which there is no load fluctuation factor such as outside temperature fluctuation or door opening / closing, and the storage chamber is stably cooled to a substantially constant temperature range.

  As shown in FIG. 7, at the elapsed time ta, the freezer compartment temperature (the temperature detected by the freezer compartment temperature sensor 34) reaches a predetermined temperature (−19 ° C.), so that the compressor ON condition is satisfied (step S108 in FIG. 6). Is Yes), the two-way valve 66 is open (step S109 in FIG. 6), and the compressor 24 is activated (step S110 in FIG. 6). At the elapsed time ta, the compressor 24 has been stopped so far, and the high-temperature refrigerant does not flow into the heat radiating pipe 64 disposed in the horizontal partition 53, so that the temperature of the horizontal partition 53 decreases and the outside The temperature is lower than the dew point temperature (here, 23.9 ° C. is the dew point temperature) based on the temperature and humidity.

  Since the three-way valve 65 is controlled to the state A at the elapsed time ta, the high temperature refrigerant flows into the heat radiating pipe 64 by the operation of the compressor, the surface of the horizontal partition 53 is heated, and the surface temperature of the horizontal partition increases. The dew point temperature is reached at the elapsed time tb. Since the compressor 24 is controlled at a high rotation speed (2400 r / min in the refrigerator 1 of the present embodiment) for 30 seconds after activation (step S110 and step S111 in FIG. 6), the horizontal partition 53 that has become low temperature is used. The surface is heated quickly. Here, the power saving mode is set, and since the refrigerator 1 is installed in an environment where the outside air temperature humidity is 30 ° C. and 70%, the switching condition of the mode ii is satisfied, and the three-way valve switching control is performed. Mode ii is selected (step S102 in FIG. 6). In mode ii, the switching condition from the three-way valve state A to the state B is satisfied when the elapsed time after the start of the compressor reaches a predetermined time t5 (= 15 minutes) (step S301 in FIG. 6). Here, the switching condition from the three-way valve state A to the state B is satisfied at the elapsed time tc, and the three-way valve is switched to the state B (step S304 in FIG. 6).

  When the three-way valve is switched to the state B, the high-temperature refrigerant does not flow in the heat radiating pipe 64, so the surface temperature of the horizontal partition portion decreases and reaches the dew point temperature at the elapsed time td. Subsequently, in mode ii, the switching condition from the state B to the state A of the three-way valve 65 is satisfied when the duration of the state B reaches t6 (step S302 in FIG. 6). Here, the switching condition from the state B to the state A of the three-way valve 65 is established at the elapsed time te, and the three-way valve is switched to the state A (step S305 in FIG. 6).

  When the three-way valve is switched to the state A, the high-temperature refrigerant flows into the heat radiating pipe 64, the horizontal partition 53 is heated, the surface temperature of the horizontal partition increases again, and reaches the dew point temperature at the elapsed time tf. Yes.

  Subsequently, in mode ii, the switching condition from the state A to the state B of the three-way valve 65 is satisfied when the duration time of the state A reaches t5 (step S301 in FIG. 6). Here, the switching condition from the state A to the state B of the three-way valve 65 is satisfied at the elapsed time tg, and the three-way valve is switched to the state B (step S304 in FIG. 6). Thereafter, the above three-way valve switching control is performed until the compressor OFF condition (step S303 in FIG. 6) is satisfied.

  At the elapsed time ti, the compressor OFF condition is satisfied. Specifically, the temperature of the freezer (not shown) (the temperature detected by the freezer temperature sensor 34), the temperature of the refrigerator (the temperature detected by the freezer temperature sensor 34), the temperature of the vegetable room ( The vegetable room temperature sensor 33a detection temperature) is the freezer room temperature −19 ° C., the refrigerator room temperature is 4 ° C., and the vegetable room temperature is 5 ° C.). Subsequently, the three-way valve is controlled to the state A (step S104 in FIG. 6). At the elapsed time ti when the duration time of state A is t1 (= 15 minutes) (step S105 in FIG. 6), the two-way valve 66 is closed (step S106 in FIG. 6), and the compressor 24 is stopped. (Step S107 in FIG. 6). Subsequently, at the elapsed time tj, the compressor ON condition is satisfied again, and the compressor 24 is operating. Thereafter, the same control is performed in the stable operation state. In addition, as shown in FIG. 7, the time average temperature of the surface of the horizontal partitioning part in the stable operation state is not more than the dew point temperature by switching control of mode ii, and in the refrigerator 1 of the present embodiment, it is 22 ° C. (dew point temperature 23.9 ° C.). It is controlled. In addition, the maximum temperature of the horizontal partition surface during the three-way valve switching control in mode ii is equal to or higher than the dew point temperature (26 ° C. in the refrigerator 1 of the present embodiment), and the minimum temperature is equal to or lower than the dew point temperature (the refrigerator of the present embodiment). 1 is 19 ° C.). Furthermore, the minimum temperature is maintained above the lower limit temperature (Tmin2).

  Incidentally, when the power saving mode setting is canceled in the refrigerator 1 of the present embodiment and the system is installed in an environment with a temperature of 30 ° C. and a relative humidity of 70% and is in a stable operation state, the switching control by the mode i is performed. The time average temperature on the surface of the horizontal partition is equal to or higher than the dew point temperature (24.3 ° C. (dew point temperature 23.9 ° C.) in the refrigerator 1 of the present embodiment).

  Although the structure of the refrigerator of this embodiment and the control method were demonstrated above, the effect which the refrigerator of this embodiment shows next is demonstrated.

  The refrigerator 1 of this embodiment is located in the back of the gap between doors, and receives a door when the door is closed to prevent ventilation between the outside and the inside of the compartment (upper heat insulating partition wall 51, lower heat insulating partition wall). 52, horizontal partition 53, vertical partition 54) and heating means (radiating pipe 64) for heating the partition, and by controlling the heating amount of the heating means for heating the partition, in a stable operation state The time average value of the partition surface temperature is set to be equal to or lower than the dew point temperature relative to the outside air temperature humidity. That is, a heat insulating box with an opening formed in the front, a plurality of doors for opening and closing the openings, and a back of a gap between the plurality of doors in contact with the door when the door is closed, A partition unit that prevents distribution; a heating unit that heats the partition unit; and a detection unit that detects a temperature and humidity of ambient air around the heat insulating box, and a time average value of the surface temperature of the partition unit is a dew point temperature. The heating means is controlled to be as follows. Thereby, the calorie | heat amount which flows in into a store | warehouse | chamber from the partition part surface can be suppressed, and the energy saving performance of a refrigerator can be improved more.

  The refrigerator 1 of this embodiment is located in the back of the gap between doors, and receives a door when the door is closed to prevent ventilation between the outside and the inside of the compartment (upper heat insulating partition wall 51, lower heat insulating partition wall). 52, horizontal partition 53, vertical partition 54) and heating means (radiating pipe 64) for heating the partition, and by controlling the heating amount of the heating means for heating the partition, in a stable operation state The time when the partition surface temperature is equal to or lower than the dew point temperature is longer than the time when the partition surface temperature is equal to or higher than the dew point temperature relative to the outside air temperature humidity. That is, a heat insulating box with an opening formed in the front, a plurality of doors for opening and closing the openings, and a back of a gap between the plurality of doors in contact with the door when the door is closed, A time for which the partition surface temperature is equal to or higher than the dew point temperature, comprising: a partition that prevents distribution; a heating unit that heats the partition; and a detection unit that detects the temperature and humidity of the ambient air around the heat insulating box. The heating means is controlled so as to increase the time during which the dew point temperature is reached. Thereby, the calorie | heat amount which flows in into a store | warehouse | chamber from the partition part surface can be suppressed, and the energy saving performance of a refrigerator can be improved more.

  The refrigerator 1 of this embodiment is based on the gap width dimension (L1 in FIG. 5) between the doors in front of the partition portions (the upper heat insulation partition wall 51, the lower heat insulation partition wall 52, the horizontal partition portion 53, and the vertical partition portion 54). The gap depth dimension (L2 in FIG. 5) extending from the door front edge to the partition surface is made larger. Thereby, it can be set as the refrigerator with which it is hard to grow dew condensation, improving a energy-saving performance by making a partition part below dew point temperature. The reason will be explained below.

  Condensation is a phenomenon in which water vapor in the outside air condenses by moving to the wall surface below the dew point temperature by convection and diffusion (mass transfer phenomenon), but especially when convection occurs near the wall surface below the dew point temperature, The nearby water vapor concentration gradient (water vapor partial pressure gradient) becomes steep, and mass transfer occurs actively. Therefore, when convection occurs, condensation grows on the wall surface below the dew point temperature in a short time and reaches a level where it flows down. Natural convection caused by density difference has a relatively small degree of mass transfer promotion.For example, when a person passes in front of a refrigerator, forced convection, that is, a flow induced by forced convection in front of the door gap. If this occurs in the gap, mass transfer is promoted, and condensation may grow in a short time.

  Therefore, in the refrigerator 1 of the present embodiment, the gap depth dimension from the door leading edge to the partition surface is larger than the gap width dimension between the doors, and the partition temperature is set to the dew point temperature or less. The influence of forced convection generated in front of the door can be kept sufficiently small. As a result, it is possible to maintain a state in which condensation does not easily grow.

  The refrigerator 1 of the present embodiment has a gap width dimension (L1 in FIG. 5) between doors in front of the upper heat insulating partition wall 51, the lower heat insulating partition wall 52, the horizontal partition portion 53, and the vertical partition portion 54, which are partition portions. The gap depth dimension (L2 in FIG. 5) from the door front edge to the partition surface is secured at least three times the gap width dimension as 10 mm or less. Natural convection also contributes to the promotion of mass transfer, although the degree of influence is small compared to forced convection. Since natural convection is unlikely to occur in a narrow space, by setting the gap width dimension between doors to 10 mm or less, it can be kept sufficiently small, and by securing a gap depth dimension that is at least three times the gap width dimension, The influence of forced convection generated in front of the door can also be suppressed sufficiently small. Thereby, the movement of water vapor is mainly due to diffusion, and the mass movement is suppressed to be sufficiently smaller than that in the case where convection occurs. Therefore, even if a partition part is made into dew point temperature or less, it can be set as the refrigerator in which condensation does not grow easily.

  The refrigerator 1 of the present embodiment controls the heating amount of the heating means disposed in the partitioning section so that the partition surface temperature alternately repeats a state above the dew point temperature of the outside air temperature humidity and a state below the dew point temperature. Thus, the time average temperature of the partition is controlled below the dew point temperature. Thereby, even if it makes a partition part below dew point temperature, it can be set as the refrigerator with which condensation does not grow easily. The reason will be described below with reference to FIG.

  FIG. 8A is a schematic diagram showing how water vapor diffuses through the gap between the doors when the partition surface temperature is equal to or lower than the dew point temperature, and FIG. 8B shows the partition surface temperature is the dew point temperature. It is a schematic diagram showing a mode that water vapor | steam diffuses in the clearance gap between doors when it is above. As shown in FIG. 8 (a), when the surface temperature of the partition portion falls below the dew point temperature, the water vapor in the vicinity of the surface of the partition portion condenses to produce minute water droplets on the surface of the partition portion. At this time, the vicinity of the partition surface becomes the saturated water vapor partial pressure Pw based on the temperature of the partition surface, and a gradient with respect to the water vapor partial pressure based on the outside air humidity is formed. The difference in the water vapor partial pressure Pw becomes the driving force for the diffusion of water vapor molecules. On the other hand, since the total pressure P (= Pw + Pa) in the gap between the doors is kept constant, the partial pressure Pa of air increases by the amount by which the water vapor partial pressure Pw decreases.

  Therefore, since the air and the pressure gradient are opposite to each other and the air tends to diffuse toward the outside of the chamber, the air acts to prevent the diffusion of the water vapor that tends to go to the partition surface. Due to this action, even if minute water droplets are generated in the initial stage, the subsequent movement of water vapor is hindered by air and the diffusion resistance of water vapor increases, so that condensation grows even when the partition surface temperature is below the dew point temperature. It becomes difficult.

  Next, when heated from the state of FIG. 8 (a) to a temperature equal to or higher than the dew point temperature shown in FIG. 8 (b), the partition surface is saturated because there are minute water droplets, and the water vapor content of the partition surface is reduced. The pressure Pw is a pressure based on the partition surface temperature. Even if the surface temperature is slightly higher than the dew point temperature, it is higher than the partial pressure Pw of the outside air, and furthermore, the diffusion direction of the water vapor is promoted because the air diffusion direction and the water vapor diffusion direction coincide. (The diffusion resistance of water vapor is reduced).

  Therefore, by controlling the heating amount of the heating means provided in the partition, the partition surface temperature is alternately repeated between a state above the dew point temperature of the outside air temperature humidity and a state below the dew point temperature. If the time average temperature is controlled below the dew point temperature, if the dew point temperature is below, the diffusion resistance will increase, making it difficult for condensation to grow, and if it exceeds the dew point temperature, the diffusion resistance will decrease. However, since water vapor is actively discharged to the outside of the warehouse, the time average temperature of the partition part is controlled to be below the dew point temperature, so that the energy saving performance is sufficiently enhanced, but substantially substantially. It can be set as the refrigerator without the growth of condensation.

  In addition, in the refrigerator 1 of this embodiment, although the timing of the switching control for making the time average value of the partition surface temperature in the stable operation state to be equal to or lower than the dew point temperature with respect to the outside air temperature and humidity is determined by time (t5 and t6). For example, the switching control timing may be determined based on the detected temperature of the partition temperature sensor 38.

  The refrigerator 1 according to the present embodiment includes heating means on the partition surface that can adjust the heating amount, and a heat insulating material is disposed on the back side of the heating means so that the heating amount is large, that is, in the heat radiating pipe 64. The temperature of the partition surface is controlled by alternately switching the state in which the high-temperature refrigerant is flowing and the state in which the heating amount is small, that is, the state in which the high-temperature refrigerant does not flow into the heat radiating pipe 64, before reaching the steady state. doing. Thereby, the calorie | heat amount which flows in in a store | warehouse | chamber by the heating of a heating means can be suppressed. The reason will be described with reference to FIG. 9 and FIG. 5 as appropriate.

FIG. 9 is a diagram showing the temperature change of the surface of the partition portion and the surface in contact with the interior (see FIG. 5 for the surface position). At t _A in FIG. 9, both the surface of the partition and the surface in contact with the interior are in a low temperature state. Then, the surface temperature of a partition part is rising quickly by making it into a heating state with the heat radiating pipe 64 which is a heating means. At this time, the temperature of the surface in contact with the inside of the partition portion gradually increases due to the heat capacity of the heat insulating material 53b disposed on the back side. Next, at t _B , the temperature of the surface in contact with the interior of the partition is switched to a non-heated state in which the high-temperature refrigerant does not flow in the heat radiating pipe 64 before reaching the steady state. Thereby, even if the temperature of the part near the heat radiating pipe 64 of the heat insulating material 53b rises, the vicinity of the surface in contact with the inside of the partition portion is not sufficiently raised. From t _B to t _C is an unheated state, and in the unheated state, the heat insulating material 53b is cooled from the surface in contact with the inside of the partition portion, the temperature is lowered, and the temperature of the surface of the partition portion is gradually lowered. As described above, by switching from the heated state to the non-heated state before the temperature of the surface in contact with the compartment of the partition reaches the steady state, the surface in contact with the interior of the partition is kept at a relatively low temperature. When heating the surface of the unit, the amount of heat flowing into the cabinet can be suppressed, and a refrigerator with high energy saving performance can be obtained. Moreover, since the temperature drop on the surface of the partition portion is moderated by the heat insulating material 53b, even if the non-heated state is longer than the heated state, the refrigerator is less likely to cause condensation.

  The refrigerator 1 of the present embodiment includes a control mode (mode i) in which the time average temperature of the partition surface in a stable operation state is equal to or higher than the dew point temperature, and a control mode (mode ii) that is equal to or lower than the dew point temperature. The mode can be selected by setting means. As a result, it is possible to select control that further improves energy saving performance even under the same temperature and humidity environment.For example, during times when there is a concern about shortage of power supply, energy consumption can be reduced by reducing power consumption. It is possible to select a mode with improved performance. Furthermore, when it is desired to improve the energy saving performance after correctly understanding the effects of the mode ii of the refrigerator 1 of the present embodiment, which is a mode with high energy saving performance, and the risk of condensation, by enabling the user to set Will be able to use.

  The refrigerator 1 of the present embodiment uses a heat radiating pipe 64 that is a part of the heat radiating means 60 of the refrigeration cycle as a heating means for the partition. That is, the heat dissipating means includes a first heat dissipating means (condenser 61, heat dissipating pipe 62) that dissipates heat outside the warehouse, and a second heat dissipating means (heat dissipating pipe 64) that heats the partition portion, A first refrigerant flow path that sequentially flows the refrigerant compressed by the compressor to the first heat radiating means and the second heat radiating means, and the first heat radiating means after circulating the refrigerant, A second refrigerant flow path (bypass pipe 63) bypassed from the outlet of the heat radiating means to the outlet of the second heat radiating means, and a flow path switching for switching the first refrigerant flow path and the second refrigerant flow path. Means (three-way valve 65), and the heat radiation amount of the second heat radiation means is controlled by the flow path switching means. Thereby, compared with the case where a heater is employed as the heating means, energy required for heating can be obtained with a high coefficient of performance (heating energy / power consumption for obtaining heating energy) by the heat pump action of the refrigeration cycle. The refrigerator has excellent energy saving performance.

  In the refrigerator 1 of the present embodiment, the rotation speed at the time of starting the compressor is set to a high rotation for a predetermined time. In the compressor operating state, when the three-way valve is switched to the state B in which the high-temperature refrigerant flows through the bypass pipe 63, the temperature of the partition portion decreases, and when the high-temperature refrigerant is switched to the state A in which the high-temperature refrigerant flows through the heat radiating pipe 64, Since the refrigerant quickly flows into the heat radiating pipe 64, the partition portion can be heated in a short time. On the other hand, since the high-temperature refrigerant does not flow in the heat radiating pipe 64 even in the compressor stopped state, the partition portion temperature is lowered similarly to the state B. When the compressor is started from this state, a time delay occurs until the inside of the heat radiating pipe 64 is sufficiently filled with the high-temperature refrigerant sent out by the compressor. Therefore, in the refrigerator 1 of the present embodiment, when the compressor is started from the compressor stopped state, the temperature rise of the partition portion is prevented from slowing down, and a good heating state by the heat radiating pipe 64 is quickly obtained. The rotation speed at the time of starting the compressor is set to a high rotation for a predetermined time. For example, in the refrigerator 1 of the present embodiment, the rotational speed is reduced to 1600 r / min after the compressor is driven at 2500 r / min for 30 seconds. That is, the rotation speed of the compressor is set to the first rotation speed for a predetermined time at the start-up, and then to the second rotation speed that is slower than the first rotation speed. Thereby, it becomes difficult for the heating by the heat radiating pipe to be insufficient after the compressor is started, and the refrigerator has a high energy saving performance and is unlikely to grow condensation.

  The refrigerator 1 of this embodiment is controlled so that a high temperature refrigerant | coolant flows in the thermal radiation pipe 64, when the temperature of a partition part reaches | attains a minimum temperature. Thereby, for example, even if the partition portion temperature tends to become low due to food residue etc. being sandwiched between the partition portion and the door and cold air leaking out of the storage chamber, the partition portion is excessively reduced. It can suppress that temperature falls and dew condensation grows up.

  In addition, this invention is not limited to each above-mentioned Example, Various modifications are included. For example, the outside air temperature sensor 36 and the outside air humidity sensor 37 may be installed anywhere as long as they are in an arrangement position capable of detecting the outside air temperature and humidity. Further, the partition temperature sensor 38 may not be installed inside the horizontal partition 53 as long as it is installed so that the partition temperature can be detected. That is, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.

1 Refrigerator 2 Refrigerated room (refrigerated temperature zone)
3 Ice making room (freezing temperature zone)
4 Upper freezer room (freezing temperature room)
5 Lower freezer compartment (freezing temperature zone)
6 Vegetable room (refrigerated temperature room)
7 Evaporator (cooling means)
8 Evaporator storage chamber 9 Blower (blower means)
DESCRIPTION OF SYMBOLS 10 Heat insulation box 11 Refrigerating room ventilation duct 16 Upper stage freezing room ventilation duct 13 Partition member 17 Freezing room return port 18 Vegetable room return duct 18a Vegetable room return duct outlet 19 Machine room 24 Compressor 26 Outside fan 33 Cold room temperature sensor 33a Vegetable room temperature sensor 34 Freezer room temperature sensor 35 Evaporator temperature sensor 36 Outside temperature sensor (detection means)
37 Outside air humidity sensor (detection means)
38 Partition temperature sensor 41 Dryer 43 Capillary tube (pressure reduction means)
51 Upper insulation partition wall (partition)
52 Lower heat insulation partition wall (partition)
53 Horizontal partition (partition)
54 Vertical partition (partition)
60 Heat dissipation means 61 Condenser (first heat dissipation means)
62 Heat radiation pipe (first heat radiation means)
63 Bypass pipe (second refrigerant flow path)
64 Heat radiation pipe (second heat radiation means)
65 Three-way valve (flow path switching means)
66 Two-way valve (refrigerant flow rate adjusting means)
67 Check valve 68 Pipe 80 Cold room damper 81 Freezer room damper

Claims (1)

A storage chamber provided in the heat insulating box and having an opening; a partition that partitions the opening; a plurality of doors that close the opening by contacting the partition; and a heating unit that heats the partition. A refrigerator with
The depth dimension of the gap between the doors is at least three times the width dimension of the gap between the plurality of doors,
The width dimension of the gap between the doors is 10 mm or less,
Detection means for detecting the temperature and humidity of the ambient air of the refrigerator;
Heating amount control means for controlling the heating amount of the heating means,
The heating means is a heat radiating pipe provided between the compressor and the decompression means,
The time during which the temperature of the partition is equal to or lower than the dew point temperature of the ambient air is longer than the time during which the temperature of the partition is equal to or lower than the dew point temperature, and the time average value of the temperature of the partition is equal to or lower than the dew point temperature of the ambient air. Ri executable der a mode for controlling the heating amount control means so that,
When the humidity of the ambient air detected by the detection means is higher than a predetermined value, the refrigerant discharged from the compressor when the compressor is in operation passes through the heat dissipation means and the pressure reduction means. refrigerators characterized that you control the heating amount control means in a state flowing in.

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