JP2018004121A - Refrigerator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerator which suppresses intrusion of heat into the refrigerator by suppressing heating of heating means while suppressing dew condensation across the entire partitioning part, which reduces the power consumption amount of a compressor, and which improves energy saving performance.SOLUTION: A refrigerator includes: a box body in which an opening is formed on a front surface; a plurality of storage chambers partitioned in the box body; a plurality of doors for opening/closing the opening; and a partition part which partitions the plurality of storage chambers and with which the door comes into contact in a closed state. The refrigerator also includes a refrigeration cycle having a compressor, heat radiation means, a dew condensation suppressor for heating the partition part, heating amount control means for adjusting the heating amount of the dew condensation suppressor, decompression means and a cooler. The dew condensation suppressor is provided on the downstream side of a refrigerant flow passage of the heat radiation means, and partition part temperature detection means is provided in the partition part heated by the dew condensation suppressor in which the refrigerant in the most downstream side flows with respect to the compressor.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a refrigerator.

  Patent Document 1 (Japanese Patent Application Laid-Open No. 2013-61089) states that “a partition portion (upper heat insulating partition) that is located in the back of a gap between doors and receives a door when the door is closed to prevent ventilation between the outside and the inside of the box. It is equipped with a heating means (heat dissipating pipe) that heats the partition, the wall, the lower heat insulating partition wall, the horizontal partition, and the vertical partition, and controls the heating amount of the heating means that heats the partition ”(Patent Literature) 1 [0066]) is described, “the partition portion temperature sensor is disposed in the horizontal partition portion so as to be in close contact with the steel plate” (see Patent Document 1 [0039]). Have been described.

JP2013-61089A

In patent document 1, a partition part temperature sensor is arrange | positioned inside a horizontal partition part, By controlling the heating amount of the heating means which heats a partition part using this partition part temperature sensor, a partition part surface in the range which does not condense The amount of heat flowing into the cabinet is suppressed, and the increase in the thermal load in the cabinet cooled by the refrigeration cycle is suppressed. This reduces the power consumption of the compressor and improves the energy saving performance.

  However, Patent Document 1 does not consider a specific arrangement position or structure of the partition temperature sensor. On the other hand, a temperature distribution may occur in the partition part. Even if control is performed so that condensation does not occur with the temperature sensor, if there is a part where the heating amount of the heating means is low and the temperature is lower than the part where the temperature sensor is provided, condensation may occur at that part. .

  Therefore, the present invention provides a refrigerator capable of controlling the heating amount of the partitioning portion, provided with a temperature sensor (temperature detection means) at an appropriate location, and heating the heating means while suppressing dew condensation over the entire partitioning portion. It aims at providing the refrigerator which suppresses the penetration | invasion of the heat | fever in a store | warehouse | chamber by suppressing and reduces the power consumption of a compressor and improves energy-saving performance.

  The present invention made in view of the above problems includes a box having an opening formed in the front, a plurality of storage chambers partitioned by the box, a plurality of doors for opening and closing the openings, and the plurality of storage chambers. A partition portion that contacts the door in a closed state, and includes a compressor, a heat radiating means, a dew condensation suppressor for heating the partition portion, and a heating amount for adjusting a heating amount of the dew condensation suppressor. In a refrigerator including a refrigeration cycle having a control means, a decompression means, and a cooler, the dew condensation suppressor is provided on the downstream side of the refrigerant flow path of the heat dissipation means, and the most downstream refrigerant is in the compressor. The refrigerator which provided the partition part temperature detection means in the said partition part heated with the said dew condensation inhibitor which flows.

  According to the present invention, by suppressing the heating of the heating means while suppressing the dew condensation over the entire partition, the heat intrusion into the cabinet is suppressed, and the power consumption of the compressor is reduced to save energy. The refrigerator which improves can be provided.

Front view of the refrigerator according to the first embodiment AA sectional view of FIG. The figure which shows arrangement | positioning of the heat radiator provided in the refrigerator of Example 1. Sectional schematic diagram of the heat insulation partition wall 28 of Example 1. Schematic of each refrigeration cycle configuration of six modes provided in the refrigerator of Example 1 Example of temperature change of partition cover 36a with time Front view of insulating partition wall 28 Detailed view of low temperature section 110 The figure which represented typically the state of the refrigerant | coolant in the heat radiation side piping of the weak 1st mode shown in FIG. Control flowchart related to the dew condensation suppressor 53 Mollier diagram illustrating the refrigerant state in each operation state of Example 1 Example of time-dependent change of partition temperature sensor 100 Schematic of the refrigeration cycle related to the refrigerator of Example 2 Mollier diagram for the refrigerator of Example 2 Front view of the refrigerator according to the third embodiment Schematic of the refrigeration cycle for the refrigerator of Example 3 The figure which shows arrangement | positioning of the heat radiator provided in the refrigerator of Example 3.

  Examples of the present invention will be described below.

  Example 1 of the refrigerator according to the present invention will be described. FIG. 1 is a front view of a refrigerator according to the first embodiment, and FIG. 2 is a cross-sectional view taken along line AA of FIG. The box 10 of the refrigerator 1 has a storage room in the order of a refrigerator compartment 2 from above, an ice making room 3 provided on the left and right, an upper freezer room 4, a lower freezer room 5, and a vegetable room 6. The refrigerator 1 includes a door that opens and closes the opening of each storage chamber. These doors open and close the opening of the refrigerating room 2, and are divided into left and right rotating refrigerating room doors 2 a and 2 b, and the ice making room 3, the upper freezing room 4, the lower freezing room 5, and the vegetable room 6. A drawer-type ice making door 3a, an upper freezer compartment door 4a, a lower freezer compartment door 5a, and a vegetable compartment door 6a that open and close, respectively. Hereinafter, the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5 are collectively referred to as a freezing chamber 7.

  The door 2a is provided with an operation unit 26 for performing an operation for setting the temperature in the cabinet. In order to fix the refrigerator 1 and the doors 2 a and 2 b, door hinges (not shown) are provided at the upper and lower parts of the refrigerator compartment 2, and the upper door hinges are covered with a door hinge cover 16.

  As shown in FIG. 2, the outside of the refrigerator 1 and the inside of the refrigerator are separated by a box 10 formed by filling a foam heat insulating material between the outer box 10 a and the inner box 10 b. In addition to the foam heat insulating material, a plurality of vacuum heat insulating materials 25 are mounted on the box 10 between a steel plate outer box 10a and a synthetic resin inner box 10b. In each storage room, the refrigerator compartment 2 is separated from the upper freezer compartment 4 and the ice making chamber 3 by the heat insulating partition wall 28, and the lower freezer compartment 5 and the vegetable compartment 6 are similarly separated by the heat insulating partition wall 29. In addition, on the front side of each storage room of the ice making room 3, the upper freezing room 4, and the lower freezing room 5, air in the freezing room 7 does not leak out of the warehouse through the gap between the doors 3a, 4a, 5a. A heat insulating partition wall 30 is provided.

The refrigerator compartment 2 is provided with a plurality of door pockets 33a, 33b, 33c and a plurality of shelves 34a, 34b, 34c, 34d inside the doors 2a, 2b, and is partitioned into a plurality of storage spaces. In the freezer compartment 7 and the vegetable compartment 6, an ice making container (not shown), an upper freezer container 4b, a lower freezer container 5b, and a vegetable compartment container 6b that are pulled out integrally with the doors 3a, 4a, 5a, 6a, respectively. A storage chamber 35 is provided above the heat insulating partition wall 28 provided. In general, the storage room 35 is often provided with a chilled room set lower than the temperature range of the refrigerator compartment 2. The temperature in the storage chamber 35 is adjusted by, for example, a dedicated air volume adjusting device (not shown) provided in the middle of the refrigeration chamber cool air duct 11 at the rear of the storage chamber 35, and the storage chamber 35 is too cold. May be heated by a temperature adjusting heater 19 provided in the lower part of the storage chamber 35.

  At the front end portions of the heat insulating partition walls 28, 30, 29 for partitioning the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6, steel plate partition covers 36a, 36b, 36c are provided, respectively. Of the box 10, the partition covers 36a, 36b, 36c and the outer box 10a with which the doors 2a, 2b, 3a, 4a, 5a, 6a abut in the closed state are referred to as opening edges. The partition covers 36a, 36b, and 36c constituting a part of the opening edge are hereinafter referred to as a partition unit 200. That is, the partition part 200 is a place where the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6 are partitioned and the doors 2a, 2b, 3a, 4a, 5a, and 6a are in contact with each other in the closed state. The partition portion 200 is configured to prevent the outside air from being opened by a gap between the doors 2a, 3b, 3a, 4a, 5a, 6a, a gap between the doors 2a, 3b, 3a, 4a, 5a, 6a and the box 10 or the like. Contact may cause condensation. For this reason, piping (refer to the dew condensation suppressor 53, FIG. 3 etc.) through which the refrigerant flows is provided in the openings near these doors. By supplying a high-temperature refrigerant discharged from the compressor 24 described later to the dew condensation suppressor 53, dew condensation on the partition portion 200 can be suppressed. The dew condensation suppressor 53 is covered with partition covers 36 a, 36 b, and 36 c that constitute the partition unit 200.

  The cooler 14 is provided in a cooler storage chamber 8 provided substantially at the back of the lower freezing chamber 5, and cold air that has exchanged heat with the cooler 14 is stored in the refrigerator compartment by an internal fan 9 provided above the cooler 14. Through the cold air duct 11, the upper freezer compartment cool air duct 12, the lower freezer compartment air duct 13, and the ice making room air duct (not shown), the refrigerating room 2, the upper freezer room 4, the lower freezer room 5, and the ice making room 3 The discharge ports 11a, 11b, 11c and 12a, 13a, 13b are sent to the respective storage chambers. The blowing of cold air to the refrigerator compartment 2 and the freezer compartment 7 is controlled by opening and closing the refrigerator compartment damper 20 and the freezer compartment damper 21.

  A radiant heater 22 is provided below the cooler 14. The drain water (melted water) generated at the time of defrosting once falls into the trough 23 and is discharged to the evaporating dish 32 provided on the upper portion of the compressor 24 through the drain hole 27. In addition to the compressor 24, a first radiator 50 and a machine room fan 54 shown in FIG. 5 are arranged in the machine room 39 provided at the lower back of the refrigerator 1.

  The refrigerator compartment temperature sensor 41, the freezer compartment temperature sensor 42, and the vegetable compartment temperature sensor 43 are provided on the rear side of the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6, respectively, and the cooler temperature is provided above the cooler 14. Sensors 40 are provided, and the temperatures of the refrigerator compartment 2, the freezer compartment 7, the vegetable compartment 6, and the cooler 14 are detected by these sensors. In addition, inside the door hinge cover 16 on the ceiling of the refrigerator 1, an outside air temperature sensor 37 and an outside air humidity sensor 38 for detecting the temperature and humidity of the outside air (outside air) are provided. As other sensors, a door sensor (not shown) for detecting the open / closed state of the doors 2a, 2b, 3a, 4a, 5a, 6a, a partition temperature sensor 100 which is a partition temperature detection means described later, and the like are also provided. Yes.

  On the upper part of the refrigerator 1, a control board 31 on which a CPU, a memory such as a ROM and a RAM, an interface circuit and the like, which are a part of the control device, is arranged. The control board 31 is connected to the refrigerator compartment temperature sensor 41, the freezer compartment temperature sensor 42, the vegetable compartment temperature sensor 43, the cooler temperature sensor 40, and the like. The compressor 24, the internal fan 9, the refrigerator compartment damper 20, the freezer compartment damper 21, the refrigerant control valve 47, which will be described later, and the like are controlled based on a program recorded in advance in the ROM.

  In the case of the refrigerating room cooling operation for cooling the refrigerating room 2, the refrigerating room damper 20 is opened, the freezing room damper 21 is closed, and the outlets 11 a, 11 b, 11 c provided in the refrigerating room cold air duct 11 are transferred to the refrigerating room 2. Cold air is sent. The cool air after cooling the refrigerator compartment 2 flows into a cool air return port (not shown) provided in the lower portion of the refrigerator compartment 2 and then returns to the cooler 14.

  In the case of the freezer compartment cooling operation for cooling the freezer compartment 7, the refrigerating compartment damper 20 is closed, the freezer compartment damper 21 is opened, and a plurality of each provided in the upper freezer compartment cool air duct 12 and the lower freezer compartment cool air duct 13. The cool air is discharged from the discharge ports 12a, 13a and 13b to cool the upper freezer compartment 4, the lower freezer compartment 5, and the ice making chamber 3, and then returns to the cooler 14 from the freezer compartment cool air return section 17.

  The temperature of the refrigerator compartment 2 and the freezer compartment 7 is detected by the refrigerator compartment temperature sensor 41 and the freezer compartment temperature sensor 42 provided in the warehouse, and the refrigerator compartment 2 and the freezer compartment 7 are simultaneously cooled according to the temperature in the warehouse. There is also an operation, and in that case, both the refrigerator compartment damper 20 and the freezer compartment damper 21 are opened, and cool air is blown to each storage compartment.

  There are various methods for cooling the vegetable compartment 6, for example, a method of sending cold air to the vegetable compartment 6 after cooling the refrigerator compartment 2, or an air volume adjusting device (not shown) dedicated to the vegetable compartment 6. There is a method in which the cold air generated by heat exchange in the cooler 14 is sent directly to the vegetable compartment 6. In the present embodiment, any method may be used for supplying cold air to the vegetable compartment 6. In the example shown in FIG. 2, the cold air that has flowed into the vegetable compartment 6 passes through the vegetable compartment cold air return duct 18 from the vegetable compartment cold air return portion 18 a provided in front of the lower part of the heat insulating partition wall 29. It flows into the cooler 14 lower part from 18b.

  FIG. 3 is a diagram illustrating the arrangement of the radiators provided in the refrigerator 1 of the first embodiment. In the first embodiment, the first heat radiator 50 (see FIG. 5), the second heat radiator 51, and the third heat radiator 52 are provided as the heat radiation means, and the dew condensation suppressor is used as the heating means for the partition portion 200. 53. The first radiator 50 is installed in a machine room 39 provided in the lower part on the back side of the refrigerator 1. The first radiator 50 of the present embodiment is a finned tube heat exchanger, and the heat radiation capability can be adjusted by the machine room fan 54 (see FIG. 5). The second radiator 51 and the third radiator 52 are heat exchangers having a steel plate outer box 10a as a heat radiating surface, and a refrigerant pipe is taped on the inner surface (inside the box body 10) of the outer box 10a. It is formed by fixing and substantially contacting with. The second radiator 51 and the third radiator 52 may be disposed along the top surface or the back surface instead of the side surface of the refrigerator 1. Moreover, although it is preferable to provide all the 1st heat radiator 50, the 2nd heat radiator 51, and the 3rd heat radiator 52, what is necessary is just to provide any one or more.

  The dew condensation suppressor 53 is a heating unit that heats the partition part 200 by heat radiation from the refrigerant in the refrigerant pipes provided inside the freezer compartment 7 and the vegetable compartment 6 around the partition part 200 and the outer box 10a. The flow direction of the refrigerant shown in FIG. 3 is the flow of the refrigerant in the weak first mode or the strong first mode, which will be described later, and the refrigerant flows from the machine chamber 39 side toward the region A above the vegetable chamber 6 from below the vegetable chamber 6. After flowing through the region B in the vicinity of the center of the freezer compartment 7 and the region C in the upper part of the freezer compartment 7 in order from the region A, it flows through the freezer compartment 7 and the vegetable compartment 6 side, and then flows toward the machine compartment 39 side. Yes. Region A, region B, and region C are dew condensation in the heat insulation partition wall 29 (partition cover 36c), heat insulation partition wall 30 (partition cover 36b), and heat insulation partition wall 28 (partition cover 36a) shown in FIGS. 1 and 2, respectively. The suppressor 53 is represented. Here, a connection part between the dew condensation suppressor 53 and the pipe 57 is a connection part d, and a connection part between the dew condensation suppressor 53 and the pipe 58 is a connection part f. In addition, although the dew condensation suppressor 53 is provided in the opening edge around freezer compartment doors 3a, 4a, 5a and the vegetable compartment door 6a so that the partition part 200 may be included, the opening edge around the refrigerator compartment 2 is included. May be provided. Moreover, the number of rooms of the refrigerator compartment 2 and the freezer compartment 7 of the refrigerator 1 is not specifically limited. Further, the door type of each storage chamber may be either a drawer type or a rotary type.

  FIG. 4 is a schematic sectional view of the heat insulating partition wall 28. A pipe for the dew condensation suppressor 53 is provided in the heat insulating partition wall 28 so as to be substantially in contact with the partition cover 36a constituting a part of the partition portion 200. The heat insulating partition wall 28 is cooled by the refrigerator compartment 2 and the freezer compartment 7 at the top and bottom, and the partition cover 36a in contact with the outside air is likely to be at a low temperature. Therefore, the refrigerant is passed through the dew condensation suppressor 53 so that the surface of the partition cover 36a is equal to or higher than the dew point temperature, and the partition cover 36a is heated by the heat flow 44 to suppress dew condensation. On the other hand, the heat of the dew condensation suppressor 53 also flows into the cabinet (mainly the freezer compartment 7) (heat flow 45).

  Similarly to the heat insulating partition wall 28, a dew condensation suppressor 53 is disposed in the heat insulating partition walls 29 and 30 including the partition covers 36b and 36c constituting the partition portion so as to substantially contact the partition covers 36b and 36c, respectively. ing.

  In this embodiment, as shown in FIG. 3, the freezing chamber 7, the side of the vegetable chamber 6, and the opening edge of the lower portion of the vegetable chamber 6 are also heated by the dew condensation suppressor 53. One of the opening edges other than these partition portions 200 is cooled by the freezer compartment 7 or the vegetable compartment 6, but the other is in contact with the outside air, so the upper and lower sides shown in FIG. 7 or the partition room 200 cooled by the vegetable compartment 6) is less likely to become a low temperature. In other words, the opening edge excluding the partition part 200 may require less heating by the dew condensation suppressor 53 than the partition part 200 (partition covers 36a, 36b, 36c). Alternatively, heating by the dew condensation suppressor 53 may not be performed.

  FIG. 5 is a schematic diagram of each refrigeration cycle configuration in six modes included in the refrigerator of the first embodiment. In the first embodiment, the six modes can be switched by the refrigerant control valve 47 which is the temperature control means of the dew condensation suppressor 53. Note that the refrigerant in the present embodiment is isobutane, and the amount of the refrigerant is 85 g.

  The refrigerator 1 generates cold air by utilizing the circulation of the refrigerant by the refrigeration cycle. A first radiator 50 is connected to a discharge side pipe 55 of the compressor 24 that compresses the refrigerant. In order from the first radiator 50, a second radiator 51, a third radiator 52, and an opening 82 on the inlet side of the refrigerant control valve 47 are connected. A valve seat 90 and a valve body 89 are provided inside the refrigerant control valve 47. The valve seat 90 is provided with openings 82, 83, 85, 86, 84 connected to the pipes 56, 57, 58, 91, 92, respectively. The refrigerant control valve 47 rotates the valve body 89 with, for example, a stepping motor (not shown) or the like, thereby switching the openings 83 to 86 that communicate with the opening 82 on the inlet side and the openings that communicate between the openings 83 to 86. This is a five-way valve that controls the refrigerant flow path. In the first embodiment, the first capillary tube 67a and the second capillary tube 67b are provided as refrigerant decompression means. Compared with the first capillary tube 67a, the second capillary tube 67b has a smaller flow resistance. Hereinafter, the first capillary tube 67a and the second capillary tube 67b may be collectively referred to as a capillary tube 67.

  In the weak first mode shown in FIG. 5A, the openings 82 and 83 are communicated and the openings 85 and 86 are communicated. The flow of the refrigerant at this time will be described. The refrigerant that has been compressed by the compressor 24 to become high temperature and high pressure flows from the discharge side pipe 55 of the compressor 24 through the first radiator 50, the second radiator 51, and the third radiator 52 to the pipe 56. To. In the weak first mode, the refrigerant that has flowed into the pipe 56 enters the refrigerant control valve 47 through the opening 82, passes through the opening 83, and flows from the refrigerant control valve 47 to the pipe 57. The refrigerant flows from the connection portion d of the dew condensation suppressor 53 connected to the pipe 57 to the region A, the region B, and the region C shown in FIG. The refrigerant enters the refrigerant control valve 47 again through the opening 85 connected to the pipe 58. The refrigerant that has flowed into the refrigerant control valve 47 flows through the pipe 91 through the groove 87 so that the opening 85 and the opening 86 communicate with each other, and then travels toward the dryer 66 and the first capillary tube 67a that is a decompression unit.

  The refrigerant that has been depressurized by the first capillary tube 67a to a low temperature and low pressure flows to the cooler 14 via the pipe 68 and exchanges heat with the air in the warehouse. Connected to the outlet side of the cooler 14 is a pipe 70 having a heat exchanging portion 69 capable of exchanging heat with the refrigerant flowing through the first capillary tube 67a by being arranged in the vicinity of the first capillary tube 67a. . The heat exchanging unit 69 can also exchange heat between the second capillary tube 67 b and the pipe 70. The refrigerant that has passed through the cooler 14 flows to the suction side of the compressor 24 through the pipe 70.

  Although details will be described later with reference to FIG. 9 and the like, the dew condensation suppressor 53 becomes a liquid phase region, and the pipes 58 and 92 and the dryer 66 on the downstream side of the dew condensation suppressor 53 are from the outside air temperature (outside air temperature). Even low-temperature refrigerant may flow. Therefore, a structure is adopted in which heat exchange with the outside air is suppressed so that the refrigerant does not absorb heat from the outside air and condensation does not occur. Specifically, the pipes 58 and 92 are not fixed to the side surface, top surface, and back surface of the outer box 10a with tape or the like, and heat exchange with the outside air via the side surface, top surface, and back surface is suppressed. Further, the total pipe length of the pipes 58 and 92 and the dryer 66 is 10% or less of the pipe length on the heat radiation side (from the discharge port of the compressor 24 to the first capillary tube 67a). By shortening to 5%, heat exchange with the outside air of the pipes 58 and 92 downstream of the dew condensation suppressor 53 and the dryer 66 is suppressed.

  Next, the weak second mode shown in FIG. In the weak second mode, the openings 82 and 86 are communicated, and the openings 83, 84, and 85 are closed. Therefore, the refrigerant that has flowed into the refrigerant control valve 47 from the opening 82 via the pipe 56 bypasses the dew condensation suppressor 53 and flows from the opening 86 to the pipe 91. The subsequent refrigerant flow is the same as in the weak first mode.

  In the weak third mode shown in FIG. 5C, the flow direction of the dew condensation suppressor 53 is reversed with respect to the weak first mode. The refrigerant that has flowed through the pipe 56 enters the refrigerant control valve 47 through the opening 82, flows through the opening 85 and the pipe 58, and travels from the connection portion f connected to the pipe 58 toward the region C side of the dew condensation suppressor 53 (see FIG. 3). . Thereafter, the refrigerant flows from the connection part d of the dew condensation suppressor 53 in the order of the pipe 57, the opening 83, the groove 88 of the refrigerant control valve 47, the opening 86, and the pipe 91. The subsequent refrigerant flow is the same as in the weak first mode and the weak second mode.

  The strong first mode, strong second mode, and strong third mode indicated by (d), (e), and (f) in FIG. 5 are weak values indicated by (a), (b), and (c) in FIG. The capillary tubes through which the refrigerant flows are different from those in the first mode, the weak second mode, and the weak third mode. Hereinafter, the weak first mode, the weak second mode, and the weak third mode using the first capillary tube 67a having the large flow resistance are set to the weak mode, and the strong first using the second capillary tube 67b having the small flow resistance is used. Mode, strong second mode, and strong third mode are called strong modes.

  In the strong first mode indicated by (d) in FIG. 5, as in the weak first mode, the refrigerant that has flowed through the pipe 56 flows in the order of the opening 82, the opening 83, the pipe 57, the dew condensation suppressor 53, and the pipe 58. Thereafter, the refrigerant flows from the opening 85 through the groove 87 to the opening 84 and travels to the pipe 92 connected to the opening 84. The refrigerant that has flowed through the pipe 92 flows through the second capillary tube 67 b and then into the pipe 68 and the cooler 14.

  The strong second mode indicated by (e) in FIG. 5 flows by bypassing the dew condensation suppressor 53 as in the weak second mode. The refrigerant that has flowed through the pipe 56 goes to the pipe 92 through the opening 82 and the opening 84 in order. The subsequent refrigerant flow is the same as in the strong first mode.

  In the strong third mode indicated by (f) in FIG. 5, the refrigerant that has flowed through the pipe 56 enters the refrigerant control valve 47 from the opening 82, and flows through the opening 85 and the pipe 58 in this order. From the connection part f connected to the region C toward the region C side of the dew condensation suppressor 53 (see FIG. 3). Thereafter, the refrigerant flows from the pipe 57 connected to the connection portion f of the dew condensation suppressor 53 through the opening 83, the groove 88 of the refrigerant control valve 47, the opening 84, and the pipe 92 in this order. The subsequent refrigerant flow is the same as in the strong first mode and the strong second mode.

  Next, basic heating control of the dew condensation suppressor 53 will be described. Here, the weak first mode and the strong first mode in which the refrigerant flows through the dew condensation suppressor 53 and heats the partition portion 200 are called heating operations, and the weak second mode and the strong second mode that bypass the dew condensation suppressor 53 are called. This is called non-heating operation. Details of the weak third mode, the strong third mode, and switching between the weak mode and the strong mode will be described later.

  FIG. 6 is an example of a change in temperature with time of the partition cover 36a. As shown in FIG. 4, the dew condensation suppressor 53 is accompanied by a heat flow 45 that heats the inside (mainly the freezer compartment 7). The heat flow 45 to the freezer compartment 7 is suppressed by switching the heating operation and suppressing the heating of the condensation suppressor 53 within a range where no condensation occurs. When heat enters the cabinet, the heat load to be cooled by the refrigeration cycle increases. Therefore, the heat flow 45 is suppressed, and the increase in the heat load to be cooled by the refrigeration cycle is suppressed, thereby reducing the power consumption of the compressor 24. Energy saving performance can be improved.

  Here, the ratio of the heating operation and the non-heating operation is controlled so that the temperature of the entire partition 200 including the partition cover 36a exceeds a predetermined temperature (for example, dew point temperature) determined according to the ambient temperature and humidity. By adjusting, heating of the dew condensation suppressor 53 is suppressed while suppressing dew condensation of the partition part 200. The partition temperature sensor 100 used for temperature control of the partition 200 will be described below.

  7A and 7B are front views of the heat insulating partition wall 28, where FIG. 7A shows a state in which a partition cover 36a is provided, and FIG. 7B shows a state in which the partition cover 36a is removed. The partition cover 36a provided on the front surface of the heat insulating partition wall 28 is provided with a low temperature portion 110 near the approximate center of the partition cover 36a. A partition temperature sensor 100 is provided in the low temperature portion 110.

  8A and 8B are detailed views of the low temperature part 110. FIG. 8A shows the entire low temperature part 110, and FIG. 8B shows details of the substrate 112 inside the low temperature part 110. FIG. The low temperature part 110 is comprised from the synthetic resin storage case 111 and the board | substrate 112 accommodated in this. The partition temperature sensor 100 described above is provided on the substrate 112. The substrate 112 is housed inside the housing case 111 to form the low temperature part 110, and the low temperature part 110 is incorporated through an attachment hole formed in the partition cover 36a. The partition temperature sensor 100 includes a detection element 101 such as a thermistor, an amplification circuit 102 for this output signal, and the like. In addition, a door opening / closing detection unit 113 including a Hall element (not shown), an amplification circuit for the output signal, and the like is mounted on the substrate 112. The door opening / closing detection unit 113 detects the opening / closing of the door by detecting the approach of a magnet provided in the packing of each door.

  Next, the reason why the low temperature part 110 provided with the partition part temperature sensor 100 is arranged in the partition cover 36a and the effect thereof will be described below.

  FIG. 9 schematically shows the state of the refrigerant in the heat-dissipation side pipe (from the discharge port of the compressor 24 to the first capillary tube 67a) in the weak first mode. The refrigerant state inside the first radiator 50 (section ac), the second radiator 51, the third radiator 52 (section cd), and the dew condensation suppressor 53 (section df) will be described. Symbols a to f shown in FIG. 9 correspond to the positions in the refrigeration cycle shown in FIG. 5A, symbol a is the discharge side of the compressor 24, and symbol b is the gas phase region. The symbol c is between the first radiator 50 and the second radiator 51, the symbol d is the connection portion d of the dew condensation suppressor 53, and the symbol e is the gas-liquid two-phase. The symbol f indicates the connection part f of the dew condensation suppressor 53, which changes from the region to the liquid phase region.

  The gas refrigerant 71 compressed by the compressor 24 and having a high temperature and a high pressure passes through the radiators 50 to 52 to release heat to the outside of the warehouse, and reaches the connection part d of the dew condensation suppressor 53 before reaching the connection part d. It reaches the liquid phase region of only the liquid refrigerant 72 through the mixed state of the liquid refrigerant 72 (gas-liquid two-phase region). Here, it becomes a gas-liquid two-phase region in the heat dissipation process in the first radiator 50, and then passes through the second radiator 51 and the third radiator 52, and then in the liquid phase region in the heat dissipation process of the dew condensation suppressor 53. become. Since heat dissipation in the liquid phase region is accompanied by a decrease in the refrigerant temperature, in the refrigerant flow of FIG. 5A, the connection part f on the outflow side is more in the connection part d on the inflow side of the dew condensation suppressor 53. The temperature goes down. Thereafter, the refrigerant flows through the dryer 66 in the liquid phase region to the capillary tube 67a.

  Therefore, the partition 200 heated by the dew condensation suppressor 53 on the downstream side is heated by the refrigerant in the liquid phase region having a lower temperature than the refrigerant in the gas phase region and the gas-liquid two phase region. This is a place where the temperature is low and the temperature tends to be low.

  In contrast, in the present embodiment, as shown in FIG. 3 and FIG. 7A, the low-temperature portion 110 is heated in the region C, that is, the refrigerant on the downstream side of the dew condensation suppressor 53. It was provided on the partition cover 36a. As shown in FIG. 3, the refrigerant is sequentially from the connection part d of the dew condensation suppressor 53 in the order of region A (partition cover 36 c), region B (partition cover 36 b), and region C (partition cover 36 a) of the partition unit 200. After flowing through the freezer compartment 7 and the vegetable compartment 6 side, it goes to the connection part f of the dew condensation suppressor 53. Since the low temperature part 110 which provides the partition part temperature sensor 100 is provided in the area C, and the area C is located on the downstream side of the dew condensation suppressor 53, it is a part that is particularly liable to become a liquid phase area. Further, when it is in the liquid phase region further upstream, the refrigerant temperature is particularly likely to be low. That is, it is a part of the partition 200 that is difficult to be heated by the dew condensation suppressor 53 and is likely to be low in temperature.

  In the present embodiment, the refrigerant in the dew condensation suppressor 53 that flows on the downstream side of the region C, that is, the opening edge on the side of the freezer compartment 7 and the vegetable compartment 6 tends to be in the liquid phase region, but FIG. 4 is used. As described above, since the opening edges other than the partition part 200 may require less heating of the dew condensation suppressor 53 as compared with the partition part 200, even the refrigerant in the liquid phase region can be sufficiently heated. As mentioned above, while partitioning the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6 which are storage compartments, it is dew condensation among the partition parts 200 which the doors 2a, 2b, 3a, 4a, 5a, 6a contact in a closed state. The region C (partition cover 36c) located on the most downstream side of the suppressor 53 is cooled by the refrigerating chamber 2 on the upper side of the partition 200 and the freezing chamber 7 on the lower side, and the refrigerant in the dew suppressor 53 is in the liquid phase region. Because it is difficult to heat at a low temperature, it is a place where the temperature tends to be low. Therefore, the low temperature part 110 provided with the partition part temperature sensor 100 is disposed in the region C, and control is performed so that no condensation occurs in the low temperature part 110. Accordingly, as described with reference to FIG. 6, while suppressing condensation over the entire partition 200, the heating of the condensation suppressor 53 is suppressed, so that heat intrusion into the freezer compartment 7 is suppressed and compression is performed. The refrigerator which reduces the power consumption of the machine 24 and improves energy-saving performance is obtained.

  In addition, although it is preferable to provide the partition part temperature sensor 100 in the partition part 200 through which the most downstream refrigerant flows among the condensation suppressors 53, the partition part temperature sensor 100 is heated at least at a portion where the refrigerant in the liquid phase region of the condensation suppressors 53 flows. The partition part 200 may be provided in the partition part temperature sensor 100.

Here, for example, when the outside air temperature is low, the range of the liquid phase region is generally expanded (e in FIG. 9 moves to the left), and the liquid phase region is likely to reach the upstream side in the dew condensation suppressor 53. Accordingly, the range of the liquid phase region changes depending on the outside air and the conditions in the storage, but considering the case where all the liquid refrigerant is collected upstream from the capillary tube 67, the pipe internal volume upstream from the capillary tube 67 is the refrigerant volume. It is sufficient to consider the range that can satisfy the enclosed amount. Specifically, the refrigerant filling amount is G [kg], the inner diameter of the pipe is d [m], the length is L [m], and the density of the liquid refrigerant is 550 [kg / m ³ ]. = (G / 550) / (d ² × circumferential ratio / 4) ”, and the pipe up to the distance L [m] from the capillary tube 67 may be in the liquid phase region. Think of it as a range. In addition, although the density of a liquid refrigerant changes with temperature, it is 530-570 kg / m < ³ > (The refrigerant | coolant condensing temperature on the thermal radiation side; 10-40 degreeC is assumed).

Further, as described above, since the refrigerant in the liquid phase region is at a lower temperature than the gas-liquid two phase region, more specifically, the temperature T53 of the piping surface of the dew condensation suppressor 53 adjacent to the partition temperature sensor 100, This can be determined by measuring the surface temperature T56 of the pipe 56 or the pipe 57 (between the third radiator 52 and the dew condensation suppressor 53). Specifically, when T53 may be 2 ° C. or more lower than T56, the part where the partition temperature sensor 100 is provided is heated at the part where the refrigerant in the liquid phase region of the dew condensation suppressor 53 flows. Can be considered.
In the refrigerator in which the refrigerant flow direction of the dew condensation suppressor 53 can be reversed as in (c) weak third mode and (f) strong third mode of the present embodiment shown in FIG. The range of the liquid phase region varies depending on the refrigerant flow direction. In this case, the refrigerant flow direction of the mode to be mainly used may be considered. In the present embodiment, the refrigerant flow direction of the mode mainly used is [(a) weak first mode time + (d) strong first mode time]> [(c) weak third mode time + (f ) Strong third mode time], (a) weak first mode and (d) strong first mode refrigerant flow direction. If the refrigerator flows mainly in the order of the areas C, B, A as in (c) the weak third mode and (f) the strong third mode, the low temperature provided with the partition temperature sensor 100 in the area A The same effect can be obtained by arranging the portion 110.

  In addition, the low temperature part 110 of the present embodiment forms an outer surface with a synthetic resin storage case 111 having a lower thermal conductivity than the partition cover 36a made of steel plate. In the partition part 200 heated by the dew condensation suppressor 53, the surface of the low temperature part 110 is a place where the temperature of the low temperature part 110 tends to be low because the temperature of the dew condensation suppressor 53 is difficult to conduct. Therefore, by detecting the temperature of the low temperature part 110 having a lower thermal conductivity than the partition cover 36a heated by the condensation suppressor 53 and suppressing the condensation of the low temperature part 110, dew condensation occurs over the entire partition part 200. Can be suppressed.

  As described above, in the present embodiment, the refrigerant in the dew condensation suppressor 53 that heats the partition 200 is in the liquid phase range, particularly between the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6 that are storage rooms. Of the partition part 200 in which the doors 2a, 2b, 3a, 4a, 5a, and 6a are in contact with each other in the closed state, in the region C (the heat insulating partition wall 28) located on the most downstream side of the dew condensation suppressor 53. A storage case 111 having a lower thermal conductivity than the partition cover 36a on the front surface of the wall 28 is provided. Thereby, the low temperature part 110 which becomes easy to become especially low temperature in the partition part 200 is comprised. The partition part temperature sensor 100 is provided in the low temperature part 110 and the heating of the dew condensation suppressor 53 that suppresses the condensation of the low temperature part 110 is controlled, so that the entire partition part 200 has a higher temperature than the low temperature part 110. In addition, dew condensation can be suppressed over the entire partition 200. That is, in the refrigerator capable of controlling the heating amount of the partition part 200, heat intrusion into the freezer compartment 7 is suppressed by suppressing the condensation controller 53 while suppressing the condensation over the entire partition part 200. Thus, a refrigerator that reduces the power consumption of the compressor 24 and improves the energy saving performance can be obtained.

  Further, as shown in FIG. 8, by providing the partition portion temperature sensor 100 on the substrate 112 in the low temperature portion 110, the following effects can also be obtained. In addition to the partition temperature sensor 100, a door opening / closing detection unit 113 is also mounted on the substrate 112. Providing a plurality of functions (temperature detection of the partition part 200 and door opening / closing detection) on one board facilitates mounting and is advantageous for cost reduction and space saving. In the present embodiment in which a hall element (not shown) is used for the door opening / closing detection unit 113, the opening / closing state of the door is detected by detecting a magnet provided in the packing of each door via the storage case 111. In order to detect, it is easy to detect opening and closing of the door by making the storage case 111 made of a synthetic resin that has less influence on the magnet than the steel plate.

  Next, control of the present embodiment using this partition temperature sensor 100 will be described. FIG. 10 is a control flowchart related to the dew condensation suppressor 53. Symbols (a) to (f) described in each mode are the same as those in FIG.

  When the power is turned on, the refrigerator 1 turns on the compressor 24 in the strong first mode (d) and starts cooling (S0). Immediately after the power is turned on, the internal temperature is high and a high cooling capacity is required. Therefore, cooling is performed using the second capillary tube 67b having a small channel resistance so that the refrigerant is easily circulated. In addition, the heating operation (first mode) is performed so that condensation does not occur in the partition 200 during operation.

In this state, cooling is performed until the compressor 24 is turned off (S1). In the present embodiment, the compressor 24 is turned off when the freezer temperature, which is the output of the freezer temperature sensor 42, becomes lower than a predetermined temperature (T _OFF ).

After the compressor 24 is turned off (S2) and turned on again (S3, S4), it is determined whether to use the weak mode or the strong mode (S5). In the present embodiment, the compressor 24 is turned on when the freezer temperature becomes equal to or higher than a predetermined temperature (T _ON ) in the control S3, and the outside air temperature is within a predetermined range (a range from _To1 to _To2 ). Is in weak mode, otherwise it is in strong mode. The reason why the strong mode is set when the outside air temperature is low (T _o1 or less) will be described later with reference to FIG. 11. However, when the outside air temperature is high (T _o2 or more), the strong mode is high as with the control S0. This is because a cooling capacity is required to facilitate circulation of the refrigerant.

Here, the case where it determines with weak mode first (S5; Yes) is demonstrated. If it determines with weak mode, it will drive | operate in (a) weak 1st mode (S6). Since the refrigerant does not flow while the compressor 24 is OFF and heating by the dew condensation suppressor 53 cannot be performed, the heating operation (a) weak first mode is set immediately after the compressor 24 is turned ON. After cooling for a while in this state, it is determined whether the weak mode is continued or changed to the strong mode (S7). The reason why this control is performed will be described later with reference to FIG. 11. In this embodiment, the temperature T _op detected by the partition temperature sensor 100 when T ₁ minute elapses after the compressor 24 ON (S 4) is T If that is the _one or more continues the weak mode, in the case of less than T ₁ is switched to the strong mode. T ₁ is determined based on the dew point temperature calculated from the outside air temperature sensor 37 and the outside air humidity sensor 38, and T ₁ is set to the dew point temperature + 1 ° C.

Here, the case where the weak mode is continued (S7; Yes) will be described. Controls S8 to S11 are controls for switching between heating operation and non-heating operation. Details will be described later with reference to FIG. When the temperature of the partition part 200 becomes sufficiently higher than the dew point temperature due to the heating operation (S8; Yes), the mode is switched to the weak second mode (S9) in order to suppress heating. In the present embodiment, when T _op is continued for T ₂ of T ₁ + 2 ° C. for t ₂ minutes, (b) the mode is switched to the weak second mode, and the heat flow 45 entering the freezer compartment 7 shown in FIG. To reduce. As described with reference to FIG. 6, by suppressing the heat flow 45, it is possible to suppress an increase in the heat load to be cooled by the refrigeration cycle and to improve the energy saving performance. Next, it is determined to switch from the non-heating operation to the heating operation (S10). In the present embodiment, when T _op is equal to or lower than T _{3 of} T ₁ -2 ° C. or when the non-heating operation state continues for t ₃ minutes or more, the heating operation ( a) Return to the weak first mode (S11). Incidentally, T ₃ may be a comparable T _1, but than T ₁ by a lower temperature, further suppressed the heat flow 45 due to condensation suppressor 53, it is possible to increase further the effect of energy efficiency improvement, the present In the embodiment, T ₃ = T ₁ −2 ° C.

This determination of control S8 to S11 is repeated until the pre-OFF condition (S12) of the compressor 24 is satisfied. OFF before the conditions of the compressor 24 and, in a state where the freezing compartment temperature reaches a predetermined temperature at which OFF the compressor 24 _{(T OFF)} from slightly higher temperature _{(T OFF_0),} in this embodiment _{T OFF_0} = T _OFF + 0.5 ° C.

  When the pre-OFF condition of the compressor 24 is satisfied (S12; Yes), the process proceeds to the (c) weak third mode (S13). When the compressor 24 is turned off, the refrigerant does not flow and cannot be heated by the dew condensation suppressor 53. Therefore, immediately before the compressor 24 is turned off, (c) the refrigerant is passed through the dew condensation suppressor 53 in the weak third mode, and the partition portion 200 is moved. By heating, dew condensation during the compressor 24 OFF is suppressed. In addition, the temperature distribution generated in the partition 200 is suppressed by setting the (a) weak first mode, which is the heating operation in the control S8 to S11, and the (c) weak third mode in which the refrigerant flow is reversed. . As described above, the region C in FIG. 3 on the downstream side of the refrigerant flow path of the dew condensation suppressor 53 is a liquid phase region and is likely to be at a lower temperature than the upstream region A. The temperature distribution in the region A and the region C is suppressed on the upstream side of the refrigerant flow path. As a result, dew condensation can be suppressed over the entire partition portion 200. And it returns to control S2 again and performs this driving | operation until the OFF conditions of the compressor 24 are satisfy | filled.

Next, the case where the mode is shifted to the strong mode in the control S5 or S7 will be described. In the present embodiment, the same control as the weak mode is performed except for the control S7 ′ for switching to the strong mode. When it is determined No in the control S5 and the control S7, (d) the process proceeds to the strong first mode (S7 ′). Even in the strong mode, the control for switching between the heating operation and the non-heating operation is performed in the controls S8 'to S11'. When the temperature of the partition part 200 becomes sufficiently higher than the dew point temperature due to the heating operation (S8 ′; Yes), the heat flow 45 in FIG. 4 is reduced by switching to the strong second mode (S9 ′) to suppress heating. The energy-saving performance is improved by suppressing the increase of the heat load that is cooled by the refrigeration cycle. When the non-heating operation is continued and the temperature of the partition portion 200 becomes low or a predetermined time elapses (S10 ′; Yes), the heating operation is returned to the (d) strong first mode. In this embodiment, the determinations of the controls S8 ′ and S10 ′ are the same as those of the controls S8 and S10, and the temperature and time used for each determination are the same as T ₂ , T ₃ , t ₂ and t _{3 in} the weak mode. However, the control may be different from the weak mode.

  Even in the strong mode, when the precondition for the compressor 24OFF is satisfied (S12 ′; Yes), (d) the strong first mode and the refrigerant flow are reversed to (f) the strong third mode (S13 ′). Condensation during the compressor 24 OFF is suppressed, and in addition, the temperature distribution generated in the partition part 200 is suppressed, and condensation is suppressed over the entire partition part 200. Then, it returns to control S2 and performs this driving | operation until the OFF conditions of the compressor 24 are satisfy | filled.

  The above is the basic control regarding the dew condensation suppressor 53 in the present embodiment. Next, details of the controls S5 and S7 and the controls S8 to S12 and their effects will be described with reference to FIGS.

  FIG. 11 is a Mollier diagram illustrating the refrigerant state in each operation state, where (a) is in the weak mode, (b) is in the strong mode, and (c) is in the case where the outside air temperature is low. . Each symbol is the same as FIG. 5A and FIG.

  In the refrigeration cycle, when the flow path resistance of the decompression means (capillary tubes 67a and 67b) increases, the liquidus region expands (the specific enthalpy difference between ef in FIG. 11 increases). That is, in the weak mode of FIG. 11A using the first capillary tube 67a having a large flow resistance, the specific enthalpy between ef is reduced more than in the strong mode of FIG. 11B. Since the decrease in the specific enthalpy in the liquid phase region represents a decrease in the temperature of the refrigerant, the decrease in the specific enthalpy in the liquid phase region is larger in FIG. That is, the amount of heating on the downstream side of the refrigerant flow path provided with the partition part 200, in particular the partition part temperature sensor 100, is reduced.

Therefore, when the humidity is high, the refrigeration cycle shown in FIG. 11A using the first capillary tube 67a may cause condensation due to insufficient heating in the vicinity of the partition temperature sensor 100. If the temperature rise of the partition temperature sensor 100 is not sufficient (T _op is less than T ₁ even after t ₁ minute has passed since the compressor 24 is turned on), the mode is shifted to the strong mode. As a result, the refrigeration cycle has a small decrease in specific enthalpy in the liquid phase region shown in FIG. To do.

Next, the reason why the strong mode is set when the outside air temperature is low (T _o1 or less) in the control S5 will be described with reference to FIG. When the outside air temperature is low, the refrigerant condensing temperature on the heat radiation side (the heat radiators 50 to 52 and the dew condensation suppressor 53) is lowered and the pressure is lowered. Therefore, as shown in FIG. The pressure difference becomes smaller. Therefore, when the outside air temperature is low (S5; No), the strong mode using the second capillary tube 67b is set, the flow resistance is reduced according to the pressure difference, and the pressure loss of the second capillary tube 67b is suppressed. Can be operated efficiently.

  Next, switching control between heating operation and non-heating operation of the partition 200 will be described. FIG. 12 is an example of a change with time of the partition temperature sensor 100. The control in weak mode shown to control S8-S12 in FIG. 10 is shown. The temperature condition of the outside air is constant, and the humidity of the outside air is low on the left side (for example, 50% relative humidity) and high on the right side (for example, 70% relative humidity). Since the humidity is high, the dew point temperature indicated by the broken line in the figure is also higher on the right side.

First, the control of this embodiment will be described in the low humidity state on the left side of FIG. A first heating operation to heat the partition portion 200 (a) weak first mode, the time _{t a} temperature _{T op} of the partition part 200 reaches the _{T 2} at the time _{t a} time _{t 2} minutes after If t _b until the temperature _{T op} continues to _{T 2} or higher, switches the control S8, S9 to (b) weak second mode of the non-heating operation. Next, when the temperature T _op reaches T _{3 at} time t _c , the control returns to the weak first mode (a) by the control S10 and S11. Thereafter, the temperature _{T op} is increased by the heating operation, the temperature _{T op} is a _{T 2} or more in again reached _{T 2} (time _t d), the time _{t d} of _{t 2} minutes after the time _{t e,} the control Switch to (b) weak second mode again by S8 and S9. This operation is continued until the compressor 24 OFF pre-condition is satisfied (the control S12 in FIG. 10 determines Yes).

Next, the high humidity shown on the right side of FIG. 12 will be described. Since the dew point temperature is high, T ₁ (dew point temperature + 1 ° C. in this embodiment), T ₂ (T ₁ + 2 ° C.), and T ₃ (T ₁ −2 ° C.) are also low humidity. The basic control is the same as when the humidity is low. A heating operation to heat the partition section 200 (a) weak first mode, reaches the temperature _{T op} of the partition part 200 to _{T 2,} the temperature _{T op} until time _{t g} of _{t 2} minutes after that time _{t f} there When it is _{T 2} or more, the control S8, S9 switches more unheated operation (b) weak second mode. Next, when the temperature _{T op} is the _{T 3} at time _{t h,} control S10, S11 returns to from (a) weak first mode. Similarly, the control S8, S9, switched again (b) weak second mode at time _{t j} of _{t 2} minutes after the time _{t i} to the temperature _{T op} reaches _{T 2.} In the present embodiment, the time t ₂ is constant, but the time t ₂ may be a function that varies depending on the temperature and humidity of the outside air, similarly to the temperatures T ₂ and T ₃ .

Here, the low-humidity on the left side of the figure 12, compared to when right high humidity, is at high temperature T _2, T ₃ towards the time of high humidity, it the temperature T _op is unlikely to reach the T _2, T ₃ Therefore, the ratio of the heating operation to the non-heating operation increases. That is, the heating amount of the partition part 200 is increased, and dew condensation is suppressed by increasing the temperature of the partition part 200. In this way, by automatically adjusting the heating amount according to the dew point temperature, it is possible to suppress dew condensation on the partition portion 200 at the time of low humidity and high humidity. In addition, since the heating of the dew condensation suppressor 53 can be further suppressed when the humidity is low than when the humidity is high, the heat flow 45 of FIG. It can be further increased.

In the present embodiment, when the temperature T _op is T ₃ , the temperature T _op may be lower than the dew point temperature, and minute condensation may temporarily occur. However, the temperature is set higher than the dew point temperature in the heating operation. As a result, the dew is vaporized and the growth of dew does not occur. Therefore, in the present embodiment, the partition portion by the dew condensation suppressor 53 is set to be lower than the dew point temperature by allowing the temperature T _op to be lower than the dew point temperature and allowing the temporary dew condensation to occur. The heating amount of 200 is suppressed, and the energy saving performance improving effect described above is enhanced.

Further, in this embodiment, for example, at time t _a of Figure 12, is also t ₂ minutes the temperature T _op of the partition part 200 reaches the T ₂ so that not switched to the non-heating operation. This is not a temperature rise rate of temperature T _op of the partition part 200 is constant as shown in FIG. 12, immediately after the heating operation switched, is the most for the temperature rise of the temperature T _op of the partition part 200 is earlier, the temperature When T _op is switched to a non-heating operation immediately after reaching the T _2, the time of heating operation is extremely short, because the heat quantity of the partition part 200 there is a possibility that condensation is insufficient arises. Therefore, by continuing the heating operation for t ₂ minutes even after the temperature T _op of the partition 200 reaches T _{2, the} heating operation can be performed for at least t ₂ minutes, and condensation due to insufficient heating of the partition 200 is suppressed. can do.

  Note that the effects shown in FIG. 9 are not limited to the control shown in FIG. 10 and subsequent figures. For example, the average temperature of the partition temperature sensor 100 may be controlled to exceed the dew point temperature.

  In addition, in the case where a plurality of pipes of the dew condensation suppressor 53 are heated at the same location of the partition part 200, the effect of the present invention can be obtained by applying the present invention to the downstream pipe.

  Embodiment 2 of the present invention will be described below. The configuration of the present embodiment can be the same as that of the first embodiment except for the following points. The second embodiment uses a refrigerant control valve 48 (expansion valve) instead of the refrigerant control valve 47 (five-way valve) as the temperature control means of the dew condensation suppressor, and the capillary tube 67 is one of the capillary tubes 67c. It is an example.

  FIG. 13 is a schematic diagram of the refrigeration cycle of the refrigerator according to the second embodiment. In the second embodiment, the pipe 56 connected to the third radiator 52 is connected to the inlet side of the refrigerant control valve 48. The refrigerant control valve 48 is an expansion valve capable of adjusting the pressure loss.

  The high-temperature and high-pressure refrigerant compressed by the compressor 24 passes from the pipe 55 on the discharge side of the compressor 24 to the pipe 56 through the first radiator 50, the second radiator 51, and the third radiator 52 in this order. Flowing. The refrigerant that has flowed through the pipe 56 enters the refrigerant control valve 48, reduces the pressure, and then travels from the refrigerant control valve 48 to the connection portion d of the dew condensation suppressor 53 connected to the pipe 93. The refrigerant of the dew condensation suppressor 53 flows in the order of the region A, the region B, and the region C shown in FIG. 3 and then flows from the connection portion f of the dew condensation suppressor 53 to the pipe 94, and the dryer 66 and the capillary tube that is a decompression unit. Head to 67c. The subsequent refrigerant flow is the same as in the first embodiment.

  FIG. 14 is a Mollier diagram of the refrigerator according to the second embodiment. The high-temperature and high-pressure refrigerant discharged from the compressor 24 (a in FIG. 14) is radiated by the first radiator 50, the second radiator 51, and the third radiator 52, and reaches the gas-liquid two-phase region. The refrigerant in the gas-liquid two-phase region that has flowed through the third radiator 52 is decompressed by the refrigerant control valve 48 in the second embodiment (d in FIG. 14). Since the temperature of the refrigerant in the gas-liquid two-phase region decreases as the pressure decreases, the temperature of the refrigerant decompressed by the refrigerant control valve 48 decreases. Thereby, since the temperature difference between the refrigerant and the partition portion 200 is reduced, the heat radiation amount of the refrigerant by the dew condensation suppressor 53 is reduced. That is, by reducing the pressure of the refrigerant upstream of the dew condensation suppressor 53, the amount of heating of the partition unit 200 by the dew condensation suppressor 53 can be reduced. Therefore, the refrigerant control valve 48 (expansion valve) of the second embodiment capable of adjusting the pressure loss can control the amount of heating of the dew condensation suppressor 53 in the same manner as the refrigerant control valve 47 of the first embodiment. Means.

  Also in this refrigerator, as shown in FIG. 14, since it is in the liquid phase region (ef in FIG. 13 and FIG. 14) on the downstream side of the refrigerant flow path, the region C (see FIG. 3) is provided with a partition temperature sensor 110 provided with a partition temperature sensor 100, and is controlled so that condensation does not occur in the low temperature section 110, thereby suppressing condensation throughout the partition 200, It is possible to obtain a refrigerator that suppresses heating of the dew condensation suppressor 53, suppresses heat from entering the freezer compartment 7, reduces power consumption of the compressor 24, and improves energy saving performance.

Specifically, instead of the heating operation, a reduced pressure operation that reduces the flow resistance of the refrigerant control valve 48 to increase the heating amount of the dew condensation suppressor 53, and a flow of the refrigerant control valve 48 instead of the non-heating operation. It is possible to control the temperature of the low temperature part 110 by providing a high pressure reduction operation that increases the road resistance and suppresses the heating amount of the dew condensation suppressor 53, and performs the control shown in the control S8 to S12 shown in FIG. it can. Alternatively, the temperature T _op of the partition portion temperature sensor 100, the dew point or higher, for example may be controlled flow resistance of the refrigerant control valve 48 so as to be constant at a temperature T ₁ of the first embodiment.

  Embodiment 3 of the present invention will be described below. The configuration of the present embodiment can be the same as that of the first embodiment except for the following points. The third embodiment is different from the first embodiment in the arrangement of the refrigerator compartment 2, the vegetable compartment 6, and the freezer compartment 7, and the condensation suppressor 53 is divided into two, the condensation suppressors 53a and 53b, and a bottom surface in the middle. This is an example in which a radiator 60 is provided.

  FIG. 15 is a front view of the refrigerator according to the third embodiment. The freezer compartment 7 is arranged on the left, the refrigerator compartment 2 on the upper right side, and the vegetable compartment 6 on the lower part. The refrigerator compartment 2, the vegetable compartment 6, and the freezer compartment 7 are provided with a rotary refrigerator compartment door 2a, a vegetable compartment door 6a, and a freezer compartment door 7a, respectively.

  FIG. 16 is a schematic diagram of the refrigeration cycle of the refrigerator according to the refrigerator 1 of the third embodiment, and FIG. 17 is a diagram showing the arrangement of the radiators provided in the refrigerator 1 of the third embodiment. Both represent (a) the state in the weak first mode. In FIG. 17, only the dew condensation suppressor 53 and the bottom radiator 60 are illustrated. In the present embodiment, the partition room 200 is a portion where the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6, which are storage compartments, are partitioned and the doors 2a, 6a, and 7a are in contact with each other in the closed state.

  As shown in FIGS. 16 and 17, the pipe 57 connected to the opening 83 of the refrigerant control valve 47 is connected to the dew condensation suppressor 53 a that heats the opening edge (including the partition portion 200) around the freezer compartment 7, and the dew condensation occurs. The outlet side of the suppressor 53a is connected to the bottom radiator 60, and the outlet side of the bottom radiator 60 is connected to the dew condensation suppressor 53b that heats the opening edges (including the partition portion 200) around the refrigerator compartment 2 and the vegetable compartment 6. Has been. The outlet side of the dew condensation suppressor 53b is connected to a pipe 58 connected to the opening 85 of the refrigerant control valve 47, similarly to the outlet side of the dew condensation suppressor 53 of the first embodiment.

Next, a specific refrigerant flow in the dew condensation suppressors 53a and 53b will be described with reference to FIG. (A) In the weak first mode, the connection part on the inlet side of the dew condensation suppressor 53a is h, the connection part on the outlet side is j, the connection part on the inlet side of the dew condensation suppressor 53b is k, and the connection on the outlet side The partition 200 between the vegetable compartment 6 and the freezer compartment 7 is the region D, the partition between the refrigerator compartment 2 and the vegetable compartment 6 is the region E, and the partition between the refrigerator compartment 2 and the freezer compartment 7 is the region. F. The refrigerant that has flowed in from the connection portion h of the dew condensation suppressor 53a passes through the opening edge on the left side of the freezer compartment 7 and the upper side of the freezer compartment 7 in order, and then the region F (between the refrigerator compartment 2 and the freezer compartment 7) and the region D (vegetable compartment 6 and Flows through the freezer compartment 7) and finally passes through the lower opening edge of the freezer compartment 7 toward the connection j. The refrigerant that has flowed out of the connection part j passes through the bottom radiator 60 and travels toward the connection part k of the dew condensation suppressor 53b. The refrigerant that has flowed into the connecting portion k first flows through the lower opening edge of the vegetable compartment 6, and includes region D (between the vegetable compartment 6 and the freezer compartment 7), region E (between the refrigerator compartment 2 and the vegetable compartment 6), region F ( The partition 200 flows in the order of the refrigerator compartment 2 and the freezer compartment 7). After that, it flows through the upper part of the refrigerating room 2 and the opening edge on the right side of the refrigerating room 2 and the vegetable room 6 and flows out from the connection part m. That is, in the refrigerator 1 according to the third embodiment, the refrigerator compartment 2, which is a storage compartment, the freezer compartment 7, and the vegetable compartment 6 are partitioned, and the regions D and E of the partition portion 200 where the doors 2a, 6a, and 7a abut in a closed state. , F, the partition located most downstream of the dew condensation suppressor 53 is the region F (between the refrigerator compartment 2 and the freezer compartment 7).
In contrast to this configuration, in the refrigerator 1 of the third embodiment, the low temperature part 110 provided with the partition temperature sensor 100 is disposed in the region F. Therefore, the partition 200 that partitions the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6, which are storage rooms, and the door 2 a, 6 a, 7 a abuts in a closed state, is a region located most downstream of the dew condensation suppressor 53. By arranging the low temperature part 110 provided with the partition part temperature sensor 100 in F,
As described with reference to FIG. 6, while suppressing dew condensation over the entire partition portion 200, by suppressing heating of the dew condensation suppressor 53, heat intrusion into the freezer compartment 7 is suppressed, and the compressor 24 A refrigerator that reduces power consumption and improves energy saving performance can be obtained.
You can get a refrigerator.

  The above is Examples 1 to 3 showing this embodiment. In addition, this invention is not limited to the Example mentioned above, Various modifications are included. For example, 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. In addition, it is possible to add, delete, and replace other configurations for a part of the configuration of the embodiment.

For example, in the first embodiment, the refrigerant control valve 47 (five-way valve) capable of switching the capillary tube 67 (adjusting the flow path resistance of the pressure reducing means) and switching between the heating operation and the non-heating operation of the dew condensation suppressor 53 is provided. Although used, the present invention is also effective in a refrigerator using a refrigerant control valve having any one function. As shown in FIGS. 6 and 12, the heating of the dew condensation suppressor 53 can be changed by controlling the ratio between the heating operation and the non-heating operation. In addition, as shown in FIG. 11, the heating amount of the dew condensation suppressor 53 also changes by adjusting the flow path resistance of the decompression means, and the heating amount of the dew condensation suppressor 53 can be reduced by reducing the flow path resistance. Become more. Specifically, as in the control S6 and S7 shown in FIG. 10, an operation using the capillary tube 67a having a large flow path resistance (weak mode) is performed, and the partition temperature sensor 100 passes the predetermined time. If it is less than the temperature T ₁ (S7; No), in the operation using a small capillary tube 67b of the flow path resistance (strong mode), by increasing the heating amount of dew condensation suppressor 53 suppresses condensation of the partition portion 200 be able to. That is, both are heating amount control means of the partition part 200, and higher energy saving performance is achieved by performing two controls ("switching of capillary tube 67" and "heating operation and non-heating operation") as in the present invention. Although the improvement effect is obtained, even in any one of the refrigerators, by controlling the heating amount of the dew condensation suppressor 53 using the partition temperature sensor 100, the partition part 200 as a whole is obtained while obtaining the energy saving performance improvement effect described above. It is possible to suppress dew condensation.

1 Refrigerator 2 Refrigerated room (storage room in refrigerated temperature zone)
2a, 2b Refrigeration room door 3 Ice making room 3a Ice making room door 4 Upper freezing room 4a Upper freezing room door 4b Upper freezing room container 5 Lower freezing room 5a Lower freezing room door 5b Lower freezing room container 6 Vegetable room 6a Vegetable room door 6b Vegetable Chamber container 7 Freezer room (freezer compartment)
8 Cooler storage chamber 9 Fan in the refrigerator 10 Heat insulation box 10a Outer box 10b Inner box 11 Refrigeration room cold air duct 11a, 11b, 11c Refrigeration room cold air outlet 12 Upper freezer cold air duct 12a Outlet 13 Lower freezer compartment cold air duct 13a 13b Discharge port 14 Cooler 16 Door hinge cover 17 Freezer compartment cool air return section 18 Vegetable compartment cold air return duct 18a Vegetable compartment cold air return portion 18b Vegetable compartment cold air return portion 19 Heater 20 Cold storage damper 21 Freezer compartment damper 22 Radiant heater 23樋 24 Compressor 25 Vacuum heat insulating material 26 Operation part 27 Drain hole 28, 29 Heat insulating partition wall 30 Heat insulating partition wall 31 Control board 32 Evaporating dishes 33a, 33b, 33c Door pockets 34a, 34b, 34c, 34d Shelf 35 Storage chamber 36a, 36b, 36c Partition cover 37 Outside temperature sensor 38 Outside humidity sensor 39 Machine room 40 Cooler temperature sensor 41 Refrigerating room temperature sensor (refrigerating room temperature)
42 Freezer temperature sensor (freezer temperature)
43 Vegetable room temperature sensor (vegetable room temperature)
44 Heat flow (outside of warehouse)
45 Heat flow (inside the warehouse)
46 Insulation partition wall 47 Refrigerant control valve (5-way valve)
48 Refrigerant control valve (expansion valve)
50 First radiator 51 Second radiator 52 Third radiator 53 Condensation suppressor 54 Machine room fan 55, 56, 57, 58, 59 Piping 66 Dryer 67a First capillary tube (pressure reducing means)
67b Second capillary tube (pressure reduction means)
68 Piping 69 Heat exchange section 70 Piping 71 Gas refrigerant 72 Liquid refrigerant 82, 83, 84, 85, 86 Opening 87, 88 Groove 89 Valve body 90 Valve seat 91, 92, 93, 94 Piping 100 Partition temperature sensor 101 Detection element 102 Amplifier circuit 110 Low temperature part 111 Storage case 112 Substrate 113 Door open / close detection part 200 Partition part

Claims (3)

A box with an opening formed in the front, a plurality of storage chambers partitioned into the box, a plurality of doors for opening and closing the openings, and partitioning the plurality of storage chambers, and the doors abutting in a closed state A partition,
A refrigerator provided with a refrigeration cycle having a compressor, a heat radiating means, a dew condensation suppressor for heating the partition, a heating amount control means for adjusting the heating amount of the dew condensation suppressor, a decompression means, and a cooler. In
The dew condensation suppressor is provided on the downstream side of the refrigerant flow path of the heat radiating means,
A refrigerator having a partition temperature detection means provided in the partition heated by the dew condensation suppressor through which the most downstream refrigerant flows relative to the compressor. A box with an opening formed in the front, a plurality of storage chambers partitioned into the box, a plurality of doors for opening and closing the openings, and partitioning the plurality of storage chambers, and the doors abutting in a closed state A partition,
A refrigerator provided with a refrigeration cycle having a compressor, a heat radiating means, a dew condensation suppressor for heating the partition, a heating amount control means for adjusting the heating amount of the dew condensation suppressor, a decompression means, and a cooler. In the above-mentioned dew condensation suppressor, the partition part temperature detection means is provided in the partition part heated in the part through which the refrigerant of the liquid phase region flows.   Provided with a low temperature part composed of a member having a lower thermal conductivity than a member that heats the outer surface in contact with the outside air substantially in contact with the dew condensation suppressor, and the partition temperature detecting means is provided inside the low temperature part The refrigerator according to claim 1 or 2, wherein the refrigerator is provided.

Images