JP7361945B2 - refrigerator - Google Patents

Description

The present disclosure relates to refrigerators.

A refrigerator has storage compartments such as a freezing compartment and a refrigerator compartment, and the storage compartment and a cooler compartment in which a cooler is installed are connected by an air path. Refrigerators generally use a fin-tube type cooler in which fins are arranged in a refrigerant tube to increase cooling capacity. The air cooled by the cooler is blown into the storage chamber through an air path by a blower, and the air inside the storage chamber is sucked back into the cooler room through another air path.

The air around the cooler is cooled by the cooler. At this time, as the temperature of the air decreases, the humidity increases, and the moisture in the air becomes frost and adheres to the surface of the cooler. This removes moisture from the air and dehumidifies the air. In this manner, cooling and dehumidification are performed simultaneously in the cooler.

A fin-tube type cooler has a refrigerant pipe through which a refrigerant flows, and the refrigerant pipe exchanges heat with the surrounding air. The refrigerant tubes are equipped with fins to increase the heat transfer area, increasing cooling capacity. The refrigerant pipe has a meandering shape, and includes a straight portion and a U-shaped bent portion. In the straight sections, thin-walled tubes are used to increase cooling capacity, and fins are arranged at a certain density. On the other hand, thick-walled pipes are used for the bends, and the bends maintain the strength of the refrigerant pipe as a whole. The side plate supports the end of the curved portion that is close to the straight portion. The curved portion of the refrigerant pipe located outside the side plate has no fins and has low cooling capacity.

The air inside the refrigerator contains outside air and water vapor from the food. For this reason, if the air passes through the cooler without being sufficiently cooled and dehumidified through the outside of the side plate, the air around the blower will be cooled down to below the dew point by the air that has flowed into the cooler chamber from the cooler freezer. Then, dew condensation occurs around the blower, and furthermore, the condensed water freezes on the operating part of the blower. As a result, the blower may not operate properly. In the refrigerator disclosed in Patent Document 1, in order to solve the above-mentioned fear, an air shielding plate is attached to the upper part of the gap outside the side plate, so that the air returned from the refrigerator compartment flows into the gap outside the side plate. is suppressed.

Patent No. 4930721

However, there is still a gap between the shield plate and the wall of the refrigerator compartment, and return air from the refrigerator compartment can still flow outside the side plate. Therefore, there is room for improvement in preventing ice from forming on the blower.

An object of the present disclosure is to provide a refrigerator in which freezing on a blower is suppressed.

The refrigerator of the present disclosure has a first storage compartment in a freezing temperature range and a second storage compartment in a second temperature range higher than the freezing temperature range, and has a difference in cooling capacity depending on the position, and cools the surrounding air. A cooler to be cooled, a cooler chamber housing the cooler, a blower disposed in the cooler chamber, the cooler chamber, and at least one of the first storage chamber or the second storage chamber are connected in front and behind each other. a first air path that sends air from the cooler room to the first storage room; a second air path that sends air from the cooler room to the second storage room; A third air path that returns air from the chamber to the cooler chamber, and a fourth air path that returns air from the second storage chamber to the cooler chamber. A circulation path is formed from the first storage room, the second storage room, the first air path, the second air path, the third air path, the fourth air path, and the cooler. The blower is disposed downstream of the cooler in the circulation path, and sends the air cooled by the cooler to the first storage room through the first air path and the second air path. The air is sent to the second storage chamber respectively, and the air is sucked from the first storage chamber and the second storage chamber through the third air path and the fourth air path, and the fourth air path is connected to the cooler. The air sucked from the second storage chamber is supplied to the first area of the cooler, and the third air passage has an air passage formed in at least a part of the partition wall and extends in the vertical direction. Air sucked from the first storage chamber is supplied to a second region having a lower cooling capacity than the first region.

The air returning from the first storage room in the freezing temperature range to the cooler room has sufficiently low temperature and humidity, and is supplied to the second area where the cooling capacity of the cooler is low, so that cooling and dehumidification by the cooler are relatively minor. However, when it reaches the blower, both the temperature and humidity are sufficiently low. On the other hand, both the temperature and humidity of the air returning from the second storage chamber to the cooler chamber are higher than the air returning from the first storage chamber to the cooler chamber. However, the air returning from the second storage chamber to the cooler chamber is alienated by the air returning from the first storage chamber to the cooler chamber and flowing through the second area, and the flow to the second area is suppressed, and the air is replaced. The air flows through the first region of the cooler having a high cooling capacity, and is sufficiently cooled and dehumidified in the first region before reaching the blower. Low-temperature, low-humidity air flows through the blower, which prevents freezing in the blower.
It is possible to provide a refrigerator in which freezing on the blower is suppressed.

A front view of a refrigerator according to Embodiment 1 of the present disclosure A sectional view taken along the line II-II in FIG. A perspective view of the partition wall of the refrigerator according to Embodiment 1 seen from the front side of the refrigerator. A perspective view of the partition wall of the refrigerator according to Embodiment 1 seen from the back side of the refrigerator. A diagram of the cooler chamber and the refrigerator compartment return air passage of the refrigerator according to Embodiment 1, viewed from the back side of the refrigerator. A diagram of the cooler compartment and refrigerator compartment return air passage of a refrigerator according to a comparative example, viewed from the back side of the refrigerator A perspective view of the partition wall of the refrigerator according to Modification Example 7 of Embodiment 1, viewed from the front side of the refrigerator. A diagram of the partition wall of the refrigerator according to Modification Example 7 of Embodiment 1, viewed from the front side of the refrigerator. A diagram of the partition wall of the refrigerator according to Modification Example 7 of Embodiment 1, viewed from the back side of the refrigerator. A cross-sectional view of the partition plate along the cross-sectional line XX in FIG. A perspective view of the partition wall of the refrigerator according to Embodiment 2, viewed from the front side of the refrigerator. A perspective view of the partition wall of the refrigerator according to Embodiment 2, viewed from the back side of the refrigerator. A diagram of the cooler chamber and the refrigerator compartment return air passage of the refrigerator according to Embodiment 2, viewed from the back side of the refrigerator. A perspective view of the partition wall of the refrigerator according to Modification 1 of Embodiment 2, seen from the front side of the refrigerator. A diagram of the partition wall of the refrigerator according to Modification 1 of Embodiment 2, viewed from the front side of the refrigerator. A diagram of the cooler chamber and the refrigerator compartment return air passage of the refrigerator according to Modified Example 1 of Embodiment 2, viewed from the back side of the refrigerator. Front view of a refrigerator according to Embodiment 3 A perspective view of the partition wall of the refrigerator according to Embodiment 3, seen from the front side of the refrigerator. A perspective view of the partition wall of the refrigerator according to Embodiment 3, viewed from the back side of the refrigerator. A diagram of the cooler chamber and the refrigerator compartment return air passage of the refrigerator according to Embodiment 3, viewed from the back side of the refrigerator. A perspective view of the partition wall of the refrigerator according to Modification 1 of Embodiment 3, seen from the front side of the refrigerator. A perspective view of the partition wall of the refrigerator according to Embodiment 4, viewed from the back side of the refrigerator. A sectional view taken along the line III-III in FIG. 22 Schematic diagram of a damper flap control section of a refrigerator according to Embodiment 4 A diagram of the cooler chamber and the refrigerator compartment return air passage of the refrigerator according to Embodiment 4, viewed from the back side of the refrigerator. A diagram of the cooler chamber and the refrigerator compartment return air passage of the refrigerator according to Embodiment 5, viewed from the back side of the refrigerator.

Hereinafter, a refrigerator according to an embodiment of the present disclosure will be described with reference to the drawings. In each figure, the same components are given the same reference numerals. In the orthogonal coordinate system XYZ shown in the figure, when the door of the refrigerator is on the front side, the left-right direction is the X-axis direction, the up-down direction is the Z-axis direction, and the direction perpendicular to the X-axis and the Z-axis is the Y-axis direction. The following description will be made using this coordinate system as appropriate. Further, in the X-axis direction, the side farthest from the center of the refrigerator or cooler is referred to as the outside.

(Embodiment 1)
Hereinafter, a refrigerator 100 according to Embodiment 1 will be described with reference to FIGS. 1 to 6. Refrigerator 100 includes a refrigerator compartment 1, as shown in FIGS. 1 and 2. The refrigerator 100 is provided with an ice-making compartment 2 on the left and a switching compartment 3 on the right side below the refrigerator compartment 1. The refrigerator 100 includes a freezing compartment 4 under the ice making compartment 2 and the switching compartment 3, and a vegetable storage compartment 5 under the freezing compartment 4, respectively.

The refrigerator compartment 1 is one of the storage compartments 15 having a space for storing stored items such as food. The temperature inside the refrigerator compartment 1 is maintained within a temperature range of +3°C to +10°C. Hereinafter, this temperature zone will be referred to as a refrigeration temperature zone. The ice making room 2 has a function of storing made ice and is one of the storage rooms 15. The ice making compartment 2 is maintained at a temperature range of -17°C or lower, for example. Hereinafter, this temperature zone will be referred to as a freezing temperature zone. In the switching room 3, the indoor temperature can be switched to a plurality of temperatures. The initial temperature is in the freezing temperature range and can be switched to a plurality of temperatures, but the temperature is lower than the temperature of the refrigerator compartment 1 and the temperature of the vegetable storage compartment 5. In this embodiment, it is assumed that the temperature is set in the freezing temperature range. Furthermore, the temperature inside the freezer compartment 4 is controlled to be within the freezing temperature range, and is one of the storage compartments 15. The vegetable storage room 5 is a space for storing vegetables, and is one of the storage rooms 15. The vegetable storage compartment 5 is maintained at a refrigerated temperature range of, for example, +3°C to +10°C.

Hereinafter, when storage compartments such as the refrigerator compartment 1 and the ice-making compartment 2 are not distinguished, they will simply be referred to as the storage compartment 15. In addition, a storage room in the freezing temperature range is called a freezing storage room or a first storage room, and a storage room in a refrigerating temperature range, which is a second temperature range higher than the freezing temperature range, is called a cold storage room or a second storage room. Sometimes called a storage room. The opening from which air blows out from the air passage is called the outlet, and the opening in the air passage when air returns through the air passage is called the return opening.

As shown in FIG. 2, the refrigerator 100 has an insulating box body 101 that is box-shaped as a whole. The heat insulating box 101 includes a plurality of storage chambers 15. The heat insulating box 101 and the doors 11, 31, 41, 51, etc. arranged at the front of each storage room 15 prevent heat from outside air from entering the storage room 15.

The insulation box body 101 is a partition that partitions the cooler room 7, the machine room 8, the cooler room 7, the ice making room 2, the switching room 3, the freezing room 4, and the vegetable storage room 5 in order to cool the inside of the refrigerator. It includes a wall 6, a blowout air path 101A that sends cold air from the cooler room 7 to the refrigerator room 1, and a return air path (not shown).

In the cooler chamber 7, a blower 71, a cooler 72, and a defrost heater 73 are arranged from above. Furthermore, a compressor 81 is arranged in the machine room 8 . The blower 71 blows the cold air generated by the cooler 72 to each storage compartment 15 through the air passage, and also sucks the air in each storage compartment 15 through the return air passage.

The refrigeration cycle that keeps the cooler 72 at a low temperature is composed of four elements: a compressor 81, a condenser and an expansion valve (not shown), and the cooler 72. These elements are connected in a ring by piping, and a refrigerant circulates through each element via the piping. The cooler 72 vaporizes the low-temperature, low-pressure liquid refrigerant sent via the expansion valve by removing heat from the surrounding air. This cools the air around the cooler 72.

As shown in FIG. 5, the cooler 72 is a fin tube type cooler, and is arranged below the blower 71. The cooler 72 has a meandering refrigerant pipe 72B in which a straight pipe 72BA and a U-shaped pipe 72BB are combined. A plurality of straight pipes 72BA of the refrigerant pipes 72B are horizontally installed vertically. A pair of left and right side plates 72AL and 72AR are vertically provided at the boundary between the straight tube 72BA and the U-shaped tube 72BB, as shown in the enlarged view at the lower left of FIG. The cooler 72 is supported by side plates 72AL and 72AR, and the shape of the cooler 72 is maintained.

Hereinafter, when looking at the refrigerator 100 from the rear side, the left side of the side plate 72AL located on the left side and the right side of the side plate 72AR located on the right side will be expressed as the outside of the side plate 72A, and the space between the left and right side plates 72A will be referred to as the outside of the side plate 72A. is expressed as the inside of the side plate 72A.

A thin-walled tube is adopted for the straight tube 72BA of the refrigerant tube 72B, that is, the straight portion of the refrigerant tube 72B, in order to improve the cooling capacity, and the fins 72C are arranged at a density to increase the heat transfer area. The cooling capacity has been improved. This area where the fins 72C are provided is an example of a first area in the cooler 72 that has a relatively high cooling capacity. The U-shaped tube 72BB of the refrigerant tube 72B, that is, the bent portion of the refrigerant tube 72B located outside the side plate 72A, is a thick-walled tube with the aim of improving the strength of the cooler 72, and is provided with fins. 72C is not provided, or is provided at a lower installation density than the straight portion. At the curved portion of the refrigerant pipe 72B where the fins 72C are installed at a low density, that is, outside the side plate 72A, the cooling capacity of the cooler 72 is equal to the cooling capacity of the cooler 72 inside the side plate 72A where the fins 72C are provided. lower than that. This region outside the side plate 72A is an example of a second region of the cooler 72 with relatively low cooling capacity.

The cooler 72 cools the surrounding air, and also removes moisture in the air by turning it into frost, thereby dehumidifying the air. When this frost thickens and adheres to the cooler 72, the cooling capacity decreases. For this reason, as shown in FIG. 2, a defrost heater 73 is arranged below the cooler 72. The defrosting heater 73 has a glass tube heater or a carbon heater. The defrost heater 73 heats the cooler 72 to evaporate frost attached to the surface.

The blowout air passage 101A is provided on the back side of the heat insulating box 101, and blows the cold air blown from the cooler chamber 7 through the blowout port 61A formed in the partition wall 6 into the refrigerator compartment 1 from the blowout port 1A. .

Further, a return air passage (not shown) is provided on the back side of the heat insulating box 101, and returns the air in the refrigerator compartment 1 to the cooler room 7 via the return air passage formed in the partition wall 6.

The partition wall 6 partitions the cooler room 7 and the refrigerator room 1, the ice making room 2, the switching room 3, the freezer room 4, and the vegetable storage room 5, and also connects the cooler room 7 and each storage room 15. Equipped with an air duct and multiple return air ducts to circulate cool air.
The configuration of the air passage included in the partition wall 6 will be described with reference to FIGS. 3 and 4.

The partition wall 6 is connected to the air outlet 101A shown in FIG. A return air path 61D shown in FIG. 4 is connected to the return air path from the refrigerator compartment 1 through a return port 61B shown in FIG. 3, and a return port 6C opens into the cooler chamber 7. Cold air is blown to the refrigerator compartment 1 through the blow-off air passage 101A, returns to the cooler compartment 7 through the air passage 61D, and is circulated between the refrigerator compartment 1 and the cooler compartment 7.
The blowout air path 101A is an example of a second air path, and the return air path from the refrigerator compartment 1 is an example of a fourth air path.

A circulation path is formed by the first storage room, the second storage room, the first air path, the second air path, the third air path, the fourth air path, and the cooler room 7. An example of this has been formed.

The partition wall 6 includes an air outlet 62A that opens into the ice making compartment 2, which is one of the first storage compartments in the freezing temperature range, and an air outlet that connects the cooler room 7 with the air outlet 62A. Furthermore, the partition wall 6 includes a return air path that connects a return port 62B that opens to the ice making compartment 2 and a return port 62C that opens to the cooler chamber 7. Air in the ice-making compartment 2 passes through return ports 62B and 62C and returns to the cooler compartment 7. Thereby, cold air is circulated between the ice making compartment 2 and the cooler compartment 7. The air outlet 62A that connects the air outlet 62A that opens into the ice making compartment 2 and the cooler chamber 7 is an example of a first air path, and the air outlet 62B that connects the air outlet 62A that opens into the ice making compartment 2 and the cooler room 7 is an example of a first air duct. The return air path that connects the return port 62C, which is the first opening that opens into the cooler chamber 7, is an example of the third air path.

Air is blown into the switching chamber 3 by a blower 71 from an air outlet 63A shown in FIG. The air in the switching chamber 3 then returns to the cooler chamber 7 through the return port 63B and the return port 63C shown in FIG.

Air is blown into the freezer compartment 4 from an air outlet 64A shown in FIG. The air in the freezer compartment 4 then returns to the cooler compartment 7 through the return port 64B and the return port 64C shown in FIG.

As shown in FIG. 3, two air outlets 64A are formed in the partition wall 6 in parallel in the Z-axis direction. The number of air outlets 64A is equal to the number of cases provided in the freezer compartment 4. The width and air blowing direction of each air outlet 64A are set according to the size and position of the corresponding case.

Air is blown into the vegetable storage room 5 from an air outlet 65A provided in the partition wall 6. The blown air passes through the return port 65B shown in FIGS. 3 and 4 and returns into the partition wall 6. The air returning from the vegetable storage compartment 5 joins the air returning from the refrigerator compartment 1 in the return air passage 61D in the partition wall 6, passes through the return port 61C shown in FIG. Return to room 7. These return ports 62C, 63C, and 64C are provided below the blower 71 and at the lower end of the cooler 72.

Next, the positional relationship between the return port of each return air path and the cooler 72 will be explained.
As shown in FIG. 5, a return air passage 61D is formed on the left side of the refrigerator 100 in the partition wall 6 when viewed from the back, and air 61F from the refrigerator compartment 1 returns thereto. On the other hand, the air that has returned from the vegetable storage compartment 5 joins the air 61F that has returned from the refrigerator compartment 1 in the return air path 61D. The air at the refrigerating temperature returned from the refrigerating compartment 1 and the vegetable storage compartment 5 flows into the cooler compartment 7 through the return port 61C. The return port 61C for air from the refrigerator compartment 1 is provided on the left side and below the cooler 72 and upstream of the air flow with respect to the cooler 72. The air flowing in from the return port 61C flows through an air path whose direction is changed by the wall 74 of the cooler chamber 7 formed obliquely at the bottom of the cooler chamber 7.

The return port 61C formed in the partition wall 6 shown in FIG. 4 is located at a position lower than the lower end of the cooler 72, that is, the lower end of the fin 72C provided at the bottom of the cooler 72, as shown in FIG. . Return air 61F passing through return air passage 61D extending downward is blown out downward from return port 61C. The return air 61F that has flowed into the cooler chamber 7 in this manner is changed direction by an inclined surface 74A that is inclined diagonally downward toward the center of the cooler chamber 7, and flows around below the cooler 72. The return air 61F then flows into the cooler 72 from the lower end and flows upward. Thereby, the return air 61F from the refrigerator compartment 1 and the vegetable storage compartment 5 can be passed between the fins 72C provided at the bottom, and heat exchange can be performed over the entire length of the cooler 72 in the Z-axis direction. I can do it.

On the other hand, the air returned from the ice making chamber 2 flows into the cooler chamber 7 through the return port 62C. The return port 62C includes a region between the right side plate 72AR and the wall 74 of the cooler chamber 7 when viewed from the back of the refrigerator 100, or faces the region and supplies air to the cooler 72. It is located upstream of the flow.

The return port 62C formed in the partition wall 6 is formed on a surface facing the −Y-axis direction, that is, a surface facing the back side of the refrigerator 100, as shown in FIG. As shown in FIG. 5, the return port 62C is formed such that its lower end is higher than the lower end of the cooler 72, that is, the lower end of the fin 72C provided at the bottom of the cooler 72. With this configuration, the return port 62C can overlap the side plate 72AR in the Z-axis direction, and the return air 62F blown out from the return port 62C can easily flow into the outside of the side plate 72AR. can do. Thereby, the return air 61F from the refrigerator compartment 1 and the vegetable storage compartment 5 can be prevented from flowing into the outside of the side plate 72AR. That is, the return air 62F flowing outside the side plate 72AR can exhibit an air curtain effect as described later.

The air returned from the switching chamber 3 flows into the cooler chamber 7 through the return port 63C. The return port 63C includes a region between the left side plate 72AL and the wall of the return air passage 61D when viewed from the back of the refrigerator 100, or faces the region and directs air to the cooler 72. Located upstream of the flow.

As shown in FIG. 4, the return port 63C as a first opening formed in the partition wall 6 is formed on a surface facing the −Y-axis direction, that is, a surface facing the back side of the refrigerator 100. . As shown in FIG. 5, the return port 63C is formed such that its lower end is higher than the lower end of the cooler 72, that is, the lower end of the fin 72C provided at the bottom of the cooler 72. With this configuration, the return port 63C can overlap the side plate 72AL in the Z-axis direction, and the return air 63F blown out from the return port 63C can easily flow into the outside of the side plate 72AL. can do. Thereby, the return air 61F from the refrigerator compartment 1 and the vegetable storage compartment 5 can be prevented from flowing into the outside of the side plate 72AL. That is, the return air 63F flowing outside the side plate 72AL can exhibit the effect of an air curtain as described later.

The air 64F returned from the freezer compartment 4 flows into the cooler compartment 7 from the return port 64C. The return port 64C is provided at a position upstream of the air flow with respect to the cooler 72 between the return ports 63C and 62C.

The return port 64C formed in the partition wall 6 is formed on a surface facing the −Y-axis direction, that is, a surface facing the back side of the refrigerator 100, as shown in FIG. As shown in FIG. 5, the return port 64C is formed such that its lower end is higher than the lower end of the cooler 72, that is, the lower end of the fin 72C provided at the bottom of the cooler 72. With such a configuration, the entire return port 64C can be directly opposed to the cooler 72, so that the return air 64F from the return port 64C can directly flow into the cooler 72 and flow upward. I can do it. Therefore, it is possible to suppress the return air 64F from flowing downward to the fins 72C. Thereby, interference between the return air 61F and the return air 64F flowing below the cooler 72 can be suppressed, and pressure loss can be suppressed from occurring.

Next, the operation of refrigerator 100 having the above configuration will be explained.
The cooler 72 cools the air in the cooler chamber 7, and the blower 71 blows the generated cold air into each storage chamber 15 through each blowing path. On the other hand, the blower 71 sucks the air in each storage chamber 15 through the return air path and supplies it to the cooler 72 . By repeating this operation, cold air is distributed to each storage chamber 15, and the temperature inside the storage chamber 15 is maintained at an appropriate temperature.

Next, how the air sucked into the cooler chamber 7, which is characteristic of this embodiment, flows through the cooler chamber 7, how is it cooled and dehumidified, and how does it reach the blower 71? I will explain about it.

As shown in FIG. 5, the air return ports 61C, 62C, 63C, and 64C provided in the partition wall 6 are all located at or near the lower end of the cooler 72, and are upstream of the air flow. The air that has flowed into the cooler chamber 7 rises within the cooler chamber 7, passes through the cooler 72, and reaches the blower 71.

The air return port 62C from the ice making compartment 2 includes the area between the right side plate 72AR and the wall 74 of the cooler compartment 7 when viewed from the back of the refrigerator 100, or is located opposite to the area. There is. Further, the air return port 63C from the switching chamber 3 includes the area between the left side plate 72AL and the wall of the return air passage 61D when viewed from the back of the refrigerator 100, or is opposite to the area. ing. Therefore, a portion of the air 62F returning from the ice making chamber 2 and the air 63F returning from the switching chamber 3 passes outside the side plate 72AR or 72AL.

The air flowing outside the side plate 72AR or 72AL is the air that has returned from the ice making compartment 2 and the switching compartment 3, and is lower in temperature and humidity than the air that has returned from the refrigerator compartment 1 and the vegetable storage compartment 5. In the area outside the side plate 72AR or 72AL, the cooling capacity is low because there is no fin 72C, but when the air reaches the blower 71, the temperature of the air is still low and low humidity, and the air does not freeze around the blower 71.

Furthermore, since the return port 64C is provided near the center of the lower end of the cooler 72, the air 64F returned from the freezer compartment 4 flows into the area where the fins 72C are provided and flows toward the blower 71.

The air 61F from the refrigerator compartment 1 and the vegetable storage compartment 5 exits from the return port 61C, is redirected by an inclined surface 74A forming a part of the wall 74 of the cooler compartment 7, and is directed to the air return port 63C. 64C and flows toward the blower 71 through the area of the gap 60. The air pressure of the air 61F is set lower than that of the air 62F, 63F, and 64F. Therefore, the gap 60 corresponds to a region of a valley of atmospheric pressure, and this region is a region inside the side plate 72A, where the fins 72C are arranged, and is an example of a first region having a relatively high cooling capacity. The air 61F returned from the refrigerator compartment 1 or the vegetable storage compartment 5 is cooled and dehumidified before reaching the blower 71 by passing between the fins 72C, and becomes low-temperature and low-humidity air.

In this embodiment, the jet pressure of air 62F and air 63F is set higher than that of air 61F, so air 63F and air 62F act like an air curtain to exclude air 61F. do the work. Therefore, the air 61F is prevented from entering the region where the air 63F or 62F flows. That is, the air 63F flows to the left side of the side plate 72AL, and the air 62F flows to the right side of the side plate 72AR, thereby suppressing the flow of the air 61F. Note that the jet pressure of the air 61F, air 62F, air 63F, and air 64F depends on the size and rotation speed of the blower 71, the length, shape, size, and position of the first to fourth air passages, and the air outlet 63A. etc., and the size, shape, position, etc. of the return port 63C, etc., and can be appropriately adjusted according to the design. For example, by reducing the size of the return port 62C through which air flows into the cooler chamber 7, the flow velocity can be increased and the pressure can be increased.

The air 61F returned from the refrigerator compartment 1 or the vegetable storage compartment 5 joins the air in the freezing temperature range returned from the ice making compartment 2, switching compartment 3, and freezing compartment 4 around the blower 71, but the air is relatively cooled. Since cooling and dehumidification are performed in the first region with high capacity, dew condensation and freezing around the blower 71 can be suppressed even if the air is cooled by the low-temperature air 64F returned from the freezer compartment 4 or the like.

Up to this point, the relationship between air flow and temperature and humidity has been described for the embodiments of the present disclosure. Next, a comparative example will be described with reference to FIG. 6, focusing on air flow and temperature/humidity. Similar to FIG. 2, FIG. 6 is a diagram of the cooler chamber 7 viewed from the back side. In the comparative example, the return port 64C for air from the freezer compartment 4 is provided near the center of the cooler 72 in the X-axis left-right direction and near the lower end of the cooler 72. Similar to the embodiment, the air with high humidity at the refrigerating temperature from the refrigerator compartment 1 and the vegetable storage compartment 5 flows into the cooler compartment 7 through the return port 61C. The return port 61C is provided outside and below the cooler 72, similarly to the embodiment. On the other hand, the air in the freezing temperature range from the ice-making compartment 2, the switching compartment 3, and the freezing compartment 4 passes through the return port 64C and returns to the cooler compartment 7 at the center of the cooler 72 in the X-axis left-right direction.

After the air 61F in the refrigeration temperature range that has flowed from the refrigerator compartment 1 and the vegetable storage compartment 5 through the air return port 61C flows into the cooler compartment 7, a part of it flows into the area outside the side plate 72A, that is, It flows through an area where there is no fin 72C. A portion of the air 61F at the refrigeration temperature passes through the cooler 72 without being cooled by the fins 72C. Then, the air 61F at the refrigerating temperature is mixed with the air 64F at the freezing temperature returned from the freezing room around the blower 71 and cooled, and the humidity increases to below the dew point, and dew condenses on the surface of the blower 71. Further, the condensed water freezes on the movable parts of the blower 71, causing a malfunction in the blower 71.

As described above, in the comparative example, high-temperature, high-humidity air flows into the region of the cooler 72 with low cooling capacity, causing ice to form on the blower 71 and causing a problem. On the other hand, in the present embodiment, low-temperature, low-humidity air is flowed into an area where the cooling capacity of the cooler 72 is relatively low, and high-temperature, high-humidity air is flowed into an area where the cooling capacity of the cooler 72 is relatively high. By flushing, the formation of ice on the blower 71 is suppressed, and the occurrence of defects in the blower 71 is suppressed.

In addition, in FIG. 5, a return air passage 61D from the refrigerator compartment 1 and a wall 74 having an inclined surface 74A at the lower left in the drawing of the cooler compartment 7 are the first wall 74 that returns air from the second storage compartment to the cooler compartment 7. This is an example of the air path No. 4.

Up to this point, the relationship between air flow and cooling has been explained. Next, the positions, sizes, shapes, and orientations of the return ports 62C, 63C, and 64C, and the configuration of the fins 72C provided on the refrigerant pipe 72B will be described, including optimal conditions.

The mutual positions of the return ports 62C and 63C with the side plate 72A will be explained.
Of the air return port 62C from the ice-making compartment 2, it is preferable that the ratio of the area outside the side plate 72A when viewed from the back of the refrigerator is 50% or more. Similarly, it is preferable that the proportion of the area of the air return port 63C from the switching chamber 3 located outside the side plate 72A when viewed from the back of the refrigerator is 50% or more.

In this way, by setting the ratio of the area outside the side plate 72A to 50% or more, it is possible to easily allow low temperature, low humidity air to flow into the area of the cooler 72 where the cooling capacity is relatively low. Thereby, the function of suppressing the air 61F at the refrigeration temperature from flowing to the outside of the side plate 72A can be strengthened. Further, as described above, the return ports 62C, 63C are formed at positions where the lower ends thereof are higher than the lower end of the cooler 72, so that the return air 62F, 63F can easily flow to the outside of the side plate 72A. By providing such characteristics regarding the positions of the return ports 62C and 63C in the X-axis direction and the Z-axis direction, it is possible to suppress the air 61F at the refrigeration temperature from flowing to the outside of the side plate 72A.

Furthermore, when air 62F and air 63F are caused to flow into the cooler chamber 7 from below the side plate 72A, the cooler 72 functions like an air curtain due to the high jet pressure of the air 62F and air 63F. It is the space below. In this case, not only is the effect of preventing the air 61F at the refrigeration temperature flowing into the outside of the side plate 72A weakened, but also the air 61F is prevented from flowing between the fins 72C via the bottom of the cooler 72. . On the other hand, in the above embodiment, the return port 62C and the return port 63C are opposed to the cooler 72 at the height where the side plate 72A exists, and the air 62F and the air 63F are supplied from the front of the cooler 72. is flowing into the country. Thereby, it is possible to suppress the air 61F at the refrigeration temperature from flowing to the outside of the side plate 72A, and it is possible to strengthen the function of causing the air 61F at the refrigeration temperature to flow in from between the fins 72C.

Next, the arrangement of the return ports 62C, 63C, and 64C will be explained.
The return port 63C and the return port 62C are provided so as to include or face the outside area of the side plate 72A, respectively, and the return port 64C is located between the return port 63C and the return port 62C. established in A gap 60 forming a part of the flow path of the air 61F flowing in from the return port 61C is provided between the return port 63C and the return port 64C on the side closer to the return port 61C.

Compared to the case where the gap 60 is provided between the return port 62C and the return port 64C, the path through which the air 61F returning at the refrigeration temperature can flow can be shortened, pressure loss can be reduced, and the air 61F can be It is easy to lead to the gap 60.

The length of the gap 60 provided between the return port 63C and the return port 64C for air from the freezer compartment 4 in the X-axis direction is equal to the length in the X-axis direction between the side plates 72A installed on the left and right sides. It is set at 10% or more and 30% or less. Thereby, the air 61F returning from the refrigerated storage compartment can be passed through the cooler 72 while suppressing the pressure loss of the air returned from the refrigerated storage compartment.

In this way, the length in the X-axis direction that should be secured in the gap 60 is secured by the length of only one gap 60, rather than by the total length of the gaps 60 provided at multiple locations. is desirable. For example, when the return port 64C is provided in the middle between the return port 62C and the return port 63C, the gap 60 is between the return port 62C and the return port 64C, and between the return port 63C and the return port 64C. It will be installed at the location. In this case, compared to the case where only one gap 60 is provided, even if the total length of the gap 60 is set to the same length, it becomes difficult for the air 61F to flow into the gap 60, and the pressure loss increases. I end up. Therefore, it is desirable to form only one gap 60 to reduce the pressure loss. Here, the gap 60 is provided between the return port 63C and the return port 64C, as described above. On the other hand, as shown in FIG. 4, there is a small portion where no opening is formed between the return port 64C and the return port 62C. However, the length of this portion in the X-axis direction where no opening is formed is so small that the air 61F cannot flow through it, and is much smaller than the length of the gap 60 in the X-axis direction.

Next, the sizes of the return ports 62C and 63C will be explained.
The size of the return port 62C from the ice making chamber 2 and the size of the return port 63C from the switching chamber 3 affect prevention of condensation and freezing on the blower 71. If the opening area is made too large, it becomes difficult to keep the air pressure high and it becomes difficult to push away the air 61F returned from the refrigerator compartment 1. If it is made too small, air cannot flow all over the outside of the side plate 72A, and air 61F returned from the refrigerator compartment 1 cannot be prevented from flowing outside the side plate 72A. Further, the optimal size depends on the size and capacity of the refrigerator 100.

Next, the return port 64C from the freezer compartment 4 will be explained. The size of the return port 64C from the freezing compartment 4 is larger than the size of the return port 62C from the ice making compartment 2 and the size of the return port 63C from the switching compartment 3, as shown in FIGS. 4 and 5. is desirable. The return port 64C shown in FIG. 5 has a longer length in the X-axis direction than the return ports 62C and 63, thereby forming an opening with a larger area. By enlarging the return port 64C, the flow velocity of the return air 64F from the freezer compartment 4 passing between the fins 72C can be reduced. Thereby, the air pressure of the return air 64F passing through the cooler 72 can be made smaller than the air pressure of the return air 62F passing outside the side plate 72A and the air pressure of the return air 63F. Note that the return air 61F from the refrigerator compartment 1 tries to pass through a place where the air pressure is low. Therefore, it is possible to prevent the return air 61F from flowing to the outside of the side plate 72A through which the return air 62F and the return air 63F, which have relatively high air pressure, flow. Moreover, even if the return air 61F from the refrigerator compartment 1 passes through the region of the return port 64C and is displaced by the air curtain effect of the return air 64F passing through the cooler 72, the return air 62F and the return air 63F pass through the region of the return port 64C and are pushed away by the air curtain effect of the return air 64F passing through the cooler 72. Flowing to the outside of the side plate 72A can be suppressed. Note that in order to increase the opening area of the return port 64C, the length in the X-axis direction is increased, but the length in the Z-axis direction is increased, that is, the height is increased to increase the return port 64C. The opening area may be made larger.

An example in which the embodiment of the present disclosure is applied to a general household refrigerator will be described. In the refrigerator 100 shown in FIG. 1, there are five storage compartments. When the total capacity of the refrigerator 100 is 400 to 550 L, its width is about 600 mm to 700 mm, and the variation in width is within ±10%. This is because it is designed to fit the width of a refrigerator space in a typical household. In accordance with the width of the refrigerator 100, the width of the cooler 72 is designed to be about 300 mm to 500 mm.

The optimal size of the air return port 62C from the ice making compartment 2 for such a household refrigerator 100 is a width of 30 mm or more and 60 mm or less, and a height of 20 mm or more and 50 mm or less. As a result, the flow velocity of the air 62F returning from the ice making compartment 2 can be kept above a certain level while suppressing the pressure loss at the air return port 62C from the ice making compartment 2, increasing ventilation resistance in the area outside the side plate 72A. be able to.

Similarly, the size of the air return port 63C from the switching chamber 3 is set such that the width is 30 mm or more and 60 mm or less, and the height is 20 mm or more and 50 mm or less. The flow velocity of the air 63F returning from the switching chamber 3 can be kept above a certain level while suppressing pressure loss, and the ventilation resistance in the area outside the side plate 72A can be increased. The area and width-to-height ratio of the air return port 62C from the ice-making compartment 2 and the air return port 63C from the switching chamber 3 do not need to be the same.

Next, the shapes of the return ports 62C and 63C will be explained.
It is desirable that the shapes of the air return port 62C from the ice-making compartment 2 and the air return port 63C from the switching chamber 3 are rectangular. By making it rectangular, the air 62F returning from the ice-making compartment 2 can be made to flow into the outside of the side plate 72A with uniform wind pressure, wind speed, flow direction, etc., and can be made to flow over the entire area outside the side plate 72A. Air 62F returning from the ice-making compartment 2 can flow. This is because the vertical width of the return port is constant regardless of the distance from the side plate 72A. Similarly, it is desirable that the air return port 63C from the switching chamber 3 is rectangular. These can prevent the air 61F returning from the refrigerator compartment 1 and the vegetable storage compartment 5 from passing outside the side plate 72A.

A return air path formed in the partition wall 6 connecting the return port 62B shown in FIG. 3 and the return port 62C shown in FIG. 4 is formed in the vertical direction. The return port 62B shown in FIG. 3 is formed in the partition wall 6 at a higher position than the return port 62C shown in FIG. As a result, the air 62F returned from the ice-making chamber 2 is rectified by passing through the vertical air passage between the return port 62B and the return port 62C, and the horizontal component of the flow velocity becomes small. As a result, a part of the air 62F flowing into the cooler 72 from the return port 62C smoothly flows upward through the right side region of the side plate 72AR, as shown in FIG.

Similarly, the return air path formed in the partition wall 6 connecting the return port 63B shown in FIG. 3 and the return port 63C shown in FIG. 4 is formed in the vertical direction. The return port 63B shown in FIG. 3 is formed in the partition wall 6 at a higher position than the return port 63C shown in FIG. As a result, the air 63F returned from the switching chamber 3 is rectified by passing through the air passage in the vertical direction between the return port 63B and the return port 63C, and the horizontal component of the flow velocity becomes small. As a result, a portion of the air 63F that has flowed into the cooler 72 from the return port 63C smoothly flows upward through the outer region of the side plate 72AL, as shown in FIG.

(Modification 1)
In the first embodiment, the case where the return port 61C from the refrigerator compartment 1 is provided on the left side when viewed from the back side of the partition wall 6 has been described using FIGS. 1 to 5. Even in the case where the air return port 61C from the refrigerator compartment 1 is formed on the right side, the positions of the air return ports 62C, 63C, and 64C from the ice making compartment 2, switching compartment 3, and freezing compartment 4, A similar effect can be obtained by adjusting the distance between them, the height and width of each return port, etc. Further, although the configuration in which the refrigerator 100 has the ice-making compartment 2 on the left side when viewed from the front and the switching compartment 3 on the right side when viewed from the front has been described using FIGS. 1 to 5, the arrangement of the ice-making compartment 2 and the switching compartment 3 is Even in the case where they are replaced, the same effect can be obtained by replacing the arrangement of the air return port 62C from the ice-making chamber 2 and the air return port 63C from the switching chamber 3.

(Modification 2)
It is preferable that each of the air outlets 6A provided in the partition wall 6 is provided with a damper that adjusts the flow rate of circulating air. By adjusting the flow rate with these dampers, the refrigerator compartment 1, the ice making compartment 2, and the switching compartment 3 can be maintained at respective set temperatures.

(Modification 3)
A configuration may be adopted in which a return air path for air from the refrigerator compartment 1 communicates with the vegetable storage compartment 5. In this case, the air blown into the refrigerator compartment 1 passes through the vegetable storage compartment 5, the air return port 65B from the vegetable storage compartment 5, and the air 61F return port 61C from the refrigerator compartment 1 to the cooler compartment 7. return.

Furthermore, it is also possible to circulate the air without passing through either the partition wall 6 or the blowing air passage 101A. Air can be circulated without using the partition wall 6 by providing an air passage, an outlet, or a return outlet using only the heat insulating box 101 of the refrigerator 100.

(Modification 4)
In FIG. 5, in order to increase the heat transfer coefficient due to the boundary layer leading edge effect of the fins 72C, the positions of the fins 72C provided on adjacent refrigerant pipes 72B are shifted in the X-axis direction by half the pitch that forms the fins 72C. It is staggered and placed. Alternatively, a configuration may be adopted in which the fins 72C are not shifted in the X-axis direction, thereby reducing the pressure loss of the air passing through the cooler 72 and making it easier for the air in the cooler chamber 7 to flow. In this way, since the air can flow easily, the burden on the blower 71 is reduced, and power consumption can be reduced. Although the air flows easily and the air does not stay near the cooler 72, the cooling capacity is lowered, but the air 61F returned from the refrigerator compartment 1 and vegetable storage compartment 5 to the cooler compartment 7 is provided with fins 72C in the refrigerant pipe 72B. Since the air passes through the first region with high cooling capacity, there is no need for the air to remain near the cooler 72 for a long time, and this configuration can be adopted. Further, in order to promote upward heat transfer in the refrigerant pipe 72B, a configuration may be adopted in which the fins 72C are joined to a plurality of pipes in the vertical direction.

(Modification 5)
Up to this point, an example has been described in which air at freezing temperature is caused to flow outside the side plate 72A. Although the present invention is not limited to this, it is preferable that the position of the air at freezing temperature or the air in the low temperature range in the refrigerator 100 returning to the cooler chamber 7 is aligned with the area of the cooler 72 having a low cooling capacity. Return air in a low temperature range, for example return air in a freezing temperature range, is flowed to a region of the cooler 72 with a relatively low cooling capacity, that is, a second region, for example, a region without fins 72C of a fin-tube type cooler. On the other hand, return air in a high temperature range, for example, return air in a refrigeration temperature range, is made to flow to a region of the cooler 72 with a high cooling capacity, that is, a first region, for example, a region where the fins 72C of a fin tube type cooler are provided. . As a result, all the air that has passed through the cooler 72 has a low temperature, and dew condensation and freezing are suppressed.

(Modification 6)
Although the positions in the height direction of the return port 61C, return port 62C, return port 63C, and return port 64C have been described with reference to FIGS. 4 and 5, the positions where these return ports are formed may be changed as appropriate. is possible.

The return port 61C described as being formed at a position lower than the lower end of the cooler 72 may be formed at the same height as the lower end of the cooler 72. Thereby, the return air 61F that has passed through the return port 61C can be made to flow into the cooler 72 without making a detour below the cooler 72. Thereby, the occurrence of pressure loss can be suppressed.

Further, the lower end of the return port 62C, which has been described as being located at a higher position than the lower end of the cooler 72, may be formed so as to be at the same height as the lower end of the cooler 72. By being positioned at the same height in this way, the return air 62F from the return port 62C can be passed between the bottom fins 72C. Thereby, heat can be exchanged with the return air 62F over the entire length of the cooler 72 in the Z-axis direction while suppressing the return air 61F from flowing to the outside of the side plate 72AR. Similarly, the return port 63C may be formed such that the lower end of the return port 63C is at the same height as the lower end of the cooler 72. Thereby, the return air 63F that has passed through the return port 63C can be heat exchanged over the entire length of the cooler 72 in the Z-axis direction while suppressing the flow of the return air 61F to the outside of the side plate 72AL.

Further, the height of the lower end of the return port 63C may be the same as the height of the lower end of the return port 62C. Thereby, it is possible to prevent unevenness in the effect of the air curtain of suppressing the return air 61F from flowing to the outside of the side plate 72AL and the outside of the side plate 72AR.

Further, the height of the lower end of the return port 64C may be the same as the height of the lower end of the cooler 72. Thereby, the return air 64F from the return port 64C can be passed between the lowest fins 72C, and heat can be exchanged over the entire length of the cooler 72 in the Z-axis direction.

(Modification 7)
In the embodiment described above, each return port is an opening provided in the partition wall 6. However, the mode of each return port is not limited to the above-mentioned one, and various functions may be added. Next, a seventh modification in which the configuration of the return port formed in the partition wall 6 is different will be described with reference to FIGS. 7 to 10.

As shown in FIGS. 7 and 8, the return port 62B that opens into the ice-making compartment 2 has a rectangular opening 66A as a second opening, and this opening 66A has a plurality of openings extending vertically and horizontally. Arranged grid members 66B are provided. Here, the vertical direction refers to the vertical direction, and the horizontal direction refers to the horizontal direction. By providing the lattice material 66B in the return port 62B in this way, the food stored in the ice making compartment 2 or small items for storing food can enter through the return port 62B and block the return air path 62D. can be prevented. Furthermore, by making the extending direction of the lattice material 66B provided at the return port 62B vertical, the air passing through the return port 62B is rectified by the lattice material 66B, and the left and right components of the air after passing through the lattice material 66B are reduced. Can be made smaller. Note that the return port 62B may be provided with a plurality of grid materials extending in the horizontal direction and arranged in the vertical direction, with the extending directions of the grid materials provided at the return port 62B being different by 90 degrees.

As shown in FIG. 8, the return port 62B is provided above and on the outside of the return port 62C that opens into the cooler chamber 7. The return port 62B and the return port 62C are connected by a return air path 62D formed in the partition wall 6. The return air passage 62D partially includes an upper and lower air passage 62DA that extends in the vertical direction. By the vertical air passage 62DA formed in this way, the air passing through the return air passage 62D is rectified, and the horizontal component of the flow velocity becomes small. Although it has been described that the return air passage 62D partially includes the upper and lower air passages 62DA formed in the vertical direction, the entire return air passage 62D may be an air passage formed in the vertical direction.

The return port 63B that opens into the switching chamber 3 has a rectangular opening 67A as a second opening, as shown in FIGS. Arranged grid members 67B are provided. In this way, by providing the lattice material 67B in the return port 63B, food items stored in the switching chamber 3 or small items for storing food materials can enter through the return port 63B and block the return air path 63D. can be prevented. Furthermore, by making the extending direction of the lattice material 67B provided at the return port 63B vertical, the air passing through the return port 63B is rectified by the lattice material 67B, and the left and right components of the air after passing through the lattice material 67B are reduced. Can be made smaller. Note that the return port 63B may be provided with a plurality of grid materials extending in the horizontal direction and arranged in the vertical direction, with the extending directions of the grid materials provided at the return port 63B being different by 90 degrees.

As shown in FIG. 8, the return port 63B is provided above and on the outside of the return port 63C that opens into the cooler chamber 7. The return port 63B and the return port 63C are connected by a return air path 63D formed in the partition wall 6. The return air passage 63D partially includes an upper and lower air passage 63DA that extends in the vertical direction. By the vertical air passage 63DA formed in this way, the air passing through the return air passage 63D is rectified, and the horizontal component of the flow velocity becomes small. Although it has been explained that the return air passage 63D partially includes the upper and lower air passages 63DA formed in the vertical direction, the entire return air passage 63D may be an air passage formed in the vertical direction.

The return port 64B that opens into the freezer compartment 4 has a rectangular opening 12 as a second opening, as shown in FIGS. 7 and 8. The return port 64B is provided in the opening 12 with a plurality of reinforcing members 13 extending vertically and arranged in the horizontal direction, and a plurality of guides 14 extending in the left-right direction and provided at intervals in the vertical direction. ing. The guides 14, which serve as guide members for guiding the air passing through the return port 64B, are plate-shaped members, and as shown in FIG. It is arranged at an angle so that it is above the direction part. Note that the reinforcing material 13 may be omitted if sufficient rigidity can be ensured for the plurality of guides 14 provided at the return port 64B.

Further, the return port 64C that opens into the cooler chamber 7 has a rectangular opening 16, as shown in FIG. As shown in FIG. 10, the return air passage 17 connecting the return port 64B and the return port 64C becomes wider in the Z-axis direction toward the rear, that is, in the −Y-axis direction. In other words, the return air path 17 becomes higher as it goes from the freezer compartment 4 to the cooler compartment 7.

The return air from the freezer compartment 4 is guided obliquely upward by the guide 14, as shown by the arrow 19 in FIG. The return air guided by the guide 14 then flows obliquely upward through the return air path 17 and passes through the return port 64C. By guiding the return air obliquely upward in this way, the return air that has passed through the return port 64C can be made to flow smoothly upward into the cooler 72 as shown in FIG. . Thereby, the pressure loss when flowing into the cooler 72 can be reduced, and the cooling performance of the refrigerator can be improved.

Note that, as shown in FIG. 10, the opening 12 of the return port 64B is partitioned upward by an upper overhang portion 20 that overhangs forward from the front surface 6B of the partition wall 6, that is, in the +Y-axis direction. Here, the front of the front surface 6B is the direction in which the freezer compartment 4 is provided. Further, the opening 12 of the return port 64B is partitioned downward by a lower overhang portion 21 that overhangs forward from the front surface 6B. The upper projecting portion 20 is inclined downwardly toward the front. On the other hand, the lower projecting portion 21 is inclined upwardly toward the front. Further, the front edge 21a of the lower overhang 21 is located further forward than the front edge 14a of the guide 14 and the front edge 20a of the upper overhang 20. That is, the amount of protrusion of the lower protrusion 21 is larger than the amount of protrusion of the upper protrusion 20.

The defrosting water generated by defrosting becomes water droplets and flows down from the front surface 6B of the partition wall 6 via the upper overhang 20 and the guide 14, and onto the upper surface of the lower overhang 21 whose front edge 21a protrudes forward. reach. The upper surface of the lower projecting portion 21 has a downward slope toward the rear, that is, from the freezer compartment 4 to the cooler compartment 7. Therefore, the water droplets that have reached the upper surface of the lower projecting portion 21 flow down toward the cooler chamber 7. Therefore, it is possible to prevent the floor surface of the freezer compartment 4 from getting wet with water droplets of the defrosting water.

(Embodiment 2)
In the first embodiment, the air in the ice-making compartment 2 was returned to the cooler compartment 7 through the partition wall 6. However, a configuration may be adopted in which the air in the ice-making compartment 2 is passed through another storage compartment, for example, the freezing compartment 4, before being returned to the cooler compartment 7. By adopting such a configuration, there is no need to form a return port for the ice-making compartment 2, the configuration of the partition wall 6 can be simplified, and the air returning from the refrigerator compartment 1 is not cooled in the partition wall 6. It has the following characteristics.

This configuration and operation will be explained using FIGS. 11 to 13. The air return port 62C from the ice-making compartment 2 opened to the outside of the side plate 72A in the first embodiment shown in FIG. 5 is replaced with a part of the air return port 64C from the freezing compartment 4 as shown in FIG. By replacing it with , the same effect as in the first embodiment can be obtained.

FIG. 11 is a perspective view of the partition wall 6 of the refrigerator 100A according to the second embodiment, viewed from the front side of the refrigerator 100A. As shown in FIG. 11, an air outlet 61A for air to the refrigerator compartment 1 and a return port 61B for air from the refrigerator compartment 1 are formed on the upper surface of the partition wall 6. In addition, on the front side of the partition wall 6, an air outlet 62A for the ice making compartment 2, an air outlet 63A for the switching chamber 3, a return port 63B for air from the switching chamber 3, and an air outlet for the freezing compartment 4 are provided. A blowout port 64A and a return port 64B for air from the freezer compartment 4 are formed. Further, the air outlet 61A has a damper (not shown) that adjusts the flow rate of air circulating in the refrigerator compartment 1, and the air outlet 62A has a damper (not shown) that adjusts the flow rate of air that circulates in the ice-making compartment 2. are each provided with a damper (not shown) that adjusts the flow rate of air circulating in the switching chamber 3. By adjusting the flow rate with these dampers, the refrigerator compartment 1, the ice making compartment 2, and the switching compartment 3 can be maintained at respective set temperatures.

FIG. 12 is a perspective view of the partition wall 6 of the refrigerator 100A according to the second embodiment, viewed from the back side of the refrigerator 100A. As shown in FIG. 12, a return port 63C for air from the switching chamber 3 and a return port 64C for air from the freezer compartment 4 are provided on the back side of the partition wall 6. Two return ports 64C for air from the freezer compartment 4 are provided. The air supplied to the switching chamber 3 and the freezing chamber 4 flows into the cooler chamber 7 from these return ports. Further, a return port 61C for air from the refrigerator compartment 1 is provided at the lower left corner when viewed from the back of the partition wall 6, and air supplied to the refrigerator compartment 1 and the vegetable storage compartment 5 flows into the cooler compartment 7. .

FIG. 13 is a diagram of the cooler chamber 7 and partition wall 6 of the refrigerator 100A according to the second embodiment, viewed from the back side of the refrigerator 100A. The difference from the first embodiment is that the air flowing outside the side plate 72AR located on the right side in FIG. 13 is air originating from the freezer compartment 4. One of the return ports 64C for the air from the freezing chamber 4 faces an area outside the side plate 72AR, and part of the air in the freezing temperature range flows outside the side plate 72AR. The air 61F returning from the refrigerator compartment 1 and the vegetable storage compartment 5 passes through the first region where the arrangement density of the fins 72C is high and the cooling capacity is high, and is sufficiently cooled and dehumidified. As a result, all the air passing through the cooler 72 becomes low temperature and low humidity, and dew condensation and freezing on the blower 71 are suppressed.

(Modification 1)
In the second embodiment, the return ports 64B and 64C from the freezer compartment 4 provided at two locations had different sizes, but they may have the same size. Further, a configuration similar to that of the guide 14 shown in FIG. 10 may be provided at each return port 64C.

As shown in FIG. 14, the partition wall 6 according to the first modification is provided with two return ports 64B that are open to the freezer compartment 4 and are arranged in the X-axis direction. The two return ports 64B have rectangular openings having approximately the same size, extend in the X-axis direction, and have a plurality of guides 22 arranged in the Z-axis direction, which is the vertical direction. The guides 22, like the guides 14 described with reference to FIG. It is arranged so that it is tilted upward. Thereby, the return air that has entered the return port 64B from the freezer compartment 4 is guided obliquely upward by the guide 22. Then, the return air guided by the guide 22 can be directly passed through the return port 64C shown in FIG. 15, which opens into the cooler chamber 7. Thereby, the return air that has passed through the return port 64C can be made to flow into the cooler 72 and smoothly flow upward as shown in FIG. 16. Thereby, pressure loss when flowing into the cooler 72 can be reduced, and cooling performance can be improved.

In addition, by providing a plurality of return ports 64B for the freezer compartment and making the size of each return port 64B about the same, the return The length of the mouth 64B in the X-axis direction can be shortened. Accordingly, since the length of the guide 22 provided at the return port 64B in the X-axis direction can be shortened, the rigidity of the guide 22 can be increased. Therefore, the guide 22 can be made difficult to bend, and it is possible to prevent foreign objects from entering through the gap between the guides 22 and fingers from entering the gap between the guides 22.

Moreover, since the air cooled in the ice making compartment 2 and the freezing compartment 4 passes through the return port 64C, more air passes through the return port 63C, through which only the air cooled in the switching chamber 3 passes. Therefore, pressure loss is likely to occur at the return port 64C. In order to suppress such pressure loss, as shown in FIG. 16, the width of the return port 64C in the Z-axis direction is made larger than the width of the return port 63C in the Z-axis direction for returning air from the switching chamber 3. The opening area of the return port 64C may be increased by increasing the size.

(Embodiment 3)
In the first and second embodiments, a refrigerator compartment 1, an ice making compartment 2, a switching compartment 3, a freezing compartment 4, and a vegetable storage compartment 5 are arranged from above. A refrigerator 100B having a configuration in which the positions of the freezer compartment 4 and the vegetable storage compartment 5 are reversed vertically will be described using FIGS. 17 to 20. This configuration tends to be preferred in households where vegetables are frequently used in cooking, but frozen ingredients are used relatively infrequently. The embodiment of the present disclosure is adopted for such a configuration.

As shown in FIG. 17, the refrigerator 100B includes a refrigerator compartment 1, an ice-making compartment 2, and a switching compartment 3 at the same positions as in the first embodiment. Unlike the first embodiment, a vegetable storage compartment 5 is provided below the ice making compartment 2 and the switching compartment 3, and a freezing compartment 4 is provided below the vegetable storage compartment 5.

FIG. 18 is a perspective view of the partition wall 6 of the refrigerator 100B according to the third embodiment, viewed from the front side of the refrigerator 100B. The partition wall 6 includes an air outlet 61A for the refrigerator compartment 1, an air return port 61B, an air outlet 62A for the ice making compartment 2, an air return port 62B, and an air outlet 62B for the air to the switching chamber 3. The air outlet 63A, the air return port 63B, the air outlet 65A to the vegetable storage compartment 5, the air return port 65B, the air outlet 64A to the freezer compartment 4, and the return port 64B. each formed. Since the vegetable storage compartment 5 is located above the freezer compartment 4, the air outlet 65A and the air return port 65B to the vegetable storage compartment 5 are the same as the air outlet 64A and the air return port to the freezer compartment 4. It is provided at an upper part compared to the opening 64B. Since the vegetable storage compartment 5 is maintained within the refrigeration temperature range, the amount of air supplied may be smaller than that of the freezing compartment 4. Therefore, the air outlet 65A to the vegetable storage compartment 5 is smaller than the air outlet 64A to the freezer compartment 4.

Further, each air outlet to the refrigerator compartment 1, ice making compartment 2, switching compartment 3, and vegetable storage compartment 5 is provided with a damper (not shown) that adjusts the flow rate of air. By adjusting the flow rate with a damper, the refrigerator compartment 1, ice making compartment 2, switching compartment 3, and vegetable storage compartment 5 can be maintained at respective set temperatures.

FIG. 19 is a perspective view of the partition wall 6 seen from the back side of the refrigerator 100B. On the back side of the partition wall 6, there are a return port 61C for air from the refrigerator compartment 1, a return port 62C for air from the ice-making compartment 2, a return port 63C for air from the switching compartment 3, and a return port for air from the freezing compartment 4. 64C is provided. Air returning from the vegetable storage compartment 5 flows into the partition wall 6 from the return port 65B, is sent to the return air path 61D, joins with the air returning from the refrigerator compartment 1, and flows into the cooler compartment 7 from the return port 61C. .

FIG. 20 is a diagram of the cooler chamber 7 and partition wall 6 of the refrigerator 100B according to the third embodiment, viewed from the back side of the refrigerator 100B. The partition wall 6 has a return port for air from each storage chamber as in the first embodiment shown in FIG. Compared to the refrigerator 100B according to the first embodiment, although the vertical relationship between the freezer compartment 4 and the vegetable storage compartment 5 is reversed, the air returned from each storage compartment is in the same position as in the first embodiment. Inflow. As described with reference to FIGS. 18 and 19, the positions of the air outlets 64A, 65A from the partition wall 6 and the air return ports 64B, 65B to the partition wall 6 are changed, but By changing the air flow path, the same inflow position can be achieved. As in the first embodiment, all the air that has passed through the cooler 72 has a low temperature, and dew condensation and freezing on the blower 71 are suppressed.

(Modification 1)
In the third embodiment, the air outlet 65A and the air return outlet 65B to the vegetable storage compartment 5 are both directed forward, that is, in the Y-axis direction, as shown in FIG. It is optional whether or not to point in the direction. For example, as shown in FIG. 21, a recess 23 is provided at the end of the partition wall 6 in the X-axis direction, and an air return port 65B directed toward the X-axis, that is, outward, is formed in the recess 23. Good too. In this way, the air outlet 65A directed in the Y-axis direction and the air return port 65B directed in the X-axis direction can be directed in different directions. Thereby, the air blown out from the air outlet 65A can be spread throughout the vegetable storage compartment 5 and then flowed into the return port 65B.

Further, as shown in FIG. 21, the air outlet 65A to the vegetable storage compartment 5 is formed closer to the end of the partition wall 6 in the -X axis direction, and the return outlet 65B is formed closer to the +X axis side of the partition wall 6. It is formed closer to the end on the direction side. In this way, by forming the air outlet 65A and the return port 65B apart from each other on both the left and right ends of the partition wall 6, the air blown out from the air outlet 65A can be distributed throughout the vegetable storage compartment 5 and then sent to the return port 65B. can be allowed to flow in. In addition, it is desirable that the air outlet 65A and the return port 65B formed in the partition wall 6 be formed in the upper part of the vegetable storage compartment 5. Thereby, the relatively warm air above the vegetable storage compartment 5 can be efficiently cooled.

Note that the directions in which the blowout port 65A and the return port 65B are formed are not limited to the case where they are made to differ by 90 degrees as described above. For example, the air outlet 65A and the return outlet 65B may be arranged so as to be 180 degrees apart from each other so as to face the outside of the partition wall 6.

(Embodiment 4)
In Embodiments 1 to 3, the case where air is made to flow through the refrigerator compartment 1 and the vegetable storage compartment 5 has been described. If the temperature and humidity of the storage compartment 15 in the refrigeration temperature range are sufficiently low, there is no need for further cooling, and there is no need to flow air from the cooler compartment 7 to the storage compartment in the refrigeration temperature range. Embodiment 4 of the present disclosure, which corresponds to such a situation, will be described using FIGS. 22 to 26.

Since no air flows into the refrigerator compartment 1 and the vegetable storage compartment 5, no air returns from the refrigerator compartment 1 and the vegetable storage compartment 5 to the cooler compartment 7. Therefore, high-temperature, high-humidity air flows outside the side plate 72A and does not condense in the blower 71, and the air 63F in the freezing temperature range that returns to the cooler chamber 7 is cooled outside the side plate 72A. There is no need to divert it to areas with low ability. In this case, the cooling capacity of the cooler 72 can be used more effectively by flowing the air 63F in the freezing temperature range to the region of the cooler 72 with a high cooling capacity, that is, inside the side plate 72A.

FIG. 22 is a perspective view of the partition wall 6 seen from the back side of the refrigerator 100C. The partition wall 6 includes an air outlet 61A for the refrigerator compartment 1, an air outlet 65A for the vegetable storage compartment 5, a return port 65B for the air from the vegetable compartment 5, and an air outlet for the refrigerator compartment 1 and the vegetable storage compartment 5. An air return port 61C, an air return port 62C from the ice-making compartment 2, an air return port 63C from the switching chamber 3, and an air return port 64C from the freezing compartment 4 are provided.

FIG. 23 is a sectional view taken along the line III--III shown in FIG. 22. As shown in FIGS. 22 and 23, a flap 62H is provided at the air return port 62C from the ice-making chamber 2, and a flap 63H is provided at the air return port 63C from the switching chamber 3. The flap 63H has a stepping motor 97 as shown in FIG.

On the other hand, a damper (not shown) is provided in each of the air outlet 61A to the refrigerator compartment 1, the air outlet 62A to the ice-making compartment 2, and the air outlet 63A to the switching chamber 3 shown in FIG. ing. A thermistor 96 is provided in the refrigerator compartment 1 and the vegetable storage compartment 5 to measure the temperature.

The machine room 8 shown in FIG. 2 has a control section 9 shown in FIG. 24 that controls the angles of the flaps 63H, 62H and the damper 99. The control unit 9 includes a processor 91, a RAM 92, a ROM 93, and an input/output interface (hereinafter referred to as I/O) 95. The processor 91 uses the RAM 92 as a work memory to execute a control program stored in a ROM (Read Only Memory) 93. A RAM (Random Access Memory) 92 functions as a work area for the processor 91 and stores programs being executed and various data. A ROM (Read Only Memory) 93 stores control programs for the flaps 62H, 63H and the damper 99, fixed data used for the control, and the like. The fixed data includes a first threshold temperature T1.

Temperature information is stored in the RAM 92 through the I/O 95 from the thermistor 96 which is a temperature information acquisition unit provided in the refrigerator compartment 1 and the vegetable storage compartment 5. The processor 91 compares the threshold temperature stored in the ROM 93 in advance with the temperature information stored in the RAM 92 of the refrigerator compartment 1 and the vegetable storage compartment 5.

When the temperature of the refrigerator compartment 1 and the vegetable storage compartment 5 is lower than the threshold temperature, a damper control signal is sent to the damper 99 to rotate the damper 99 and close the damper 99. At the same time, a flap control signal is sent to the stepping motor 97 of the flap 63H and the stepping motor 98 of the flap 62H to direct the flap 63H diagonally to the right and direct the flap 62H diagonally to the left. As a result, as shown in FIG. 25, the air that passes through the return port 63C and returns to the cooler chamber 7 flows diagonally to the right, and the air that passes through the return port 62C and returns to the cooler chamber 7 flows diagonally to the left. The air 62F and 63F in the freezing temperature range flows through a region of the cooler 72 having a high cooling capacity, and is cooled with high efficiency.

If the temperature of the refrigerator compartment 1 and the vegetable storage compartment 5 is higher than the threshold temperature, a control signal from the processor 91 opens the damper 99, allowing the cooled air to flow into the second storage compartment, which is maintained at the refrigeration temperature. It is sent by a blower 71. At the same time, stepping motors 97 and 98 are rotated by a control signal from processor 91, and flaps 62H and 63H are respectively tilted outward. Air flowing in from the return port 62C or the return port 63C flows to the right side of the right side plate 72AR or to the left side of the left side plate 72AL. As in the first embodiment, the air 61F returning from the refrigerator compartment 1 and the vegetable storage compartment 5 flows through a region of the cooler 72 having a high cooling capacity, so that dew condensation and freezing on the blower 71 are suppressed.

(Embodiment 5)
In Embodiments 1 to 4, the return air passage 61D for air from the refrigerator compartment 1 is provided at the left end of the partition wall 6 when viewed from the back of the refrigerator. When the capacity of the refrigerator compartment 1 is large, return air passages 61D for air from the refrigerator compartment 1 are provided on both the left and right sides of the partition wall 6. The configuration and operation of the present disclosure in this case will be described using FIG. 26.

FIG. 26 is a diagram of the cooler chamber 7 and partition wall 6 of the refrigerator 100D viewed from the back side of the refrigerator 100D. Return air passages 61D from the refrigerator compartment 1 are formed on both the left and right sides of the partition wall 6. An example is shown in which the amount of air flowing into the return air path 61D located on the left side of the drawing is larger than the amount of air flowing into the return air path 61D located on the right side. Of the left and right return air passages 61D, it is preferable to widen the gap 60A on the side closer to the side where the amount of air flowing in is large, and narrow or eliminate the gap 60B on the side closer to the side where the amount of air flowing in is smaller. This is because the path through which the returning air 61F flows in the refrigeration temperature range can be shortened, and pressure loss can be reduced. Since the pressure loss is small, there is no need to increase the blowing pressure, and the power input to the blower 71 can be kept small. As a result, condensation or freezing on the blower 71 can be suppressed, and power consumption of the refrigerator 100D can be suppressed.

The present disclosure is a refrigerator that circulates air, and a cooler cools the circulating air. This can be applied when the cooler has a region with relatively high cooling capacity and a region with relatively low cooling capacity. Freezing temperature air is passed through the parts of the cooler with relatively low cooling capacity, and relatively high temperature and high humidity air is passed through parts with high cooling capacity. For example, the technology of the present disclosure can be applied not only to fin tube type refrigerators but also to refrigerators using Peltier elements as coolers. For example, the cooling capacity of the end portion of the Peltier element is relatively low.

The freezing temperature range is not limited to the above-mentioned temperature of −17° C. or lower. The refrigeration temperature zone is not limited to the above-described temperature range of +3° C. to +10° C., but refers to a temperature zone in the refrigerator 100 that is higher than the freezing temperature zone.

Although this disclosure discloses an example in which the refrigerating temperature and the freezing temperature are set as the temperature of the storage room, the present disclosure is not limited to this, and the application is applicable to a refrigerator in which air at the freezing temperature and air at a higher temperature circulate. can.

The present disclosure is capable of various embodiments and modifications without departing from the broad spirit and scope of the present disclosure. Moreover, the embodiments described above are for explaining this disclosure, and do not limit the scope of this disclosure. That is, the scope of the present disclosure is indicated by the claims rather than the embodiments. Various modifications made within the scope of the claims and the meaning of the disclosure equivalent thereto are considered to be within the scope of this disclosure.

This application is based on Japanese Patent Application No. 2020-185464, filed on November 5, 2020. The entire specification, claims, and drawings of Japanese Patent Application No. 2020-185464 are incorporated herein by reference.

1 Refrigerator room, 1A Air outlet, 2 Ice making room, 3 Switching room, 4 Freezer room, 5 Vegetable storage room, 6 Partition wall, 6A Air outlet, 6B Front, 6C Return port, 7 Cooler room, 8 Machine room, 9 Control part, 11 Door, 12 Opening, 13 Reinforcing material, 14 Guide, 14a Front edge, 15 Storage room, 16 Opening, 17 Return air passage, 20 Upper overhang, 20a Front edge, 21 Lower overhang, 21a Front Edge, 22 Guide, 25 Guide, 31 Door, 41 Door, 51 Door, 60 Gap, 60A Gap, 60B Gap, 61A Air outlet, 61B Return port, 61C Return port, 61D Return air path, 61F Air, 62A Air outlet, 62B return port, 62C return port, 62D return air path, 62F air, 62H flap, 62DA up and down air path, 63A air outlet, 63B return port, 63C return port, 63D return air path, 63F air, 63H flap, 63DA up and down air channel, 64A outlet, 64B return port, 64C return port, 64F air, 65A outlet, 65B return port, 66A opening, 66B lattice material, 67A opening, 67B lattice material, 71 blower, 72 cooler, 72A, 72AL, 72AR side plate, 72B refrigerant pipe, 72BA pipe, 72BB U-shaped tube, 72C fin, 73 defrost heater, 74 cooler room wall, 74A slope, 81 compressor, 91 processor, 92 RAM, 93 ROM, 96 thermistor, 97, 98 Stepping motor, 99 Damper, 100, 100A, 100B, 100C, 100D Refrigerator, 101 Insulating box, 102 Insulating door for storage room

Claims (17)

a first storage chamber in a freezing temperature zone; a second storage chamber in a second temperature zone higher than the freezing temperature zone;
A cooler that cools the surrounding air with different cooling capacities depending on its location,
a cooler chamber that houses the cooler;
a blower disposed within the cooler chamber;
a partition wall that partitions the cooler chamber and at least one of the first storage chamber and the second storage chamber into front and rear;
a first air path that sends air from the cooler chamber to the first storage chamber, a second air path that sends air from the cooler chamber to the second storage chamber, and the first storage chamber. a third air path that returns air from the storage chamber to the cooler chamber, and a fourth air path that returns air from the second storage chamber to the cooler chamber;
Equipped with
the first storage chamber, the second storage chamber, the first air path, the second air path, the third air path, the fourth air path, and the cooling Form a circulation path from the vessel,
The blower is disposed on the air downstream side of the cooler in the circulation path, and blows the air cooled by the cooler through the first air path and the second air path. Sending air to the first storage chamber and the second storage chamber, respectively, and suctioning air from the first storage chamber and the second storage chamber via the third air path and the fourth air path. death,
The fourth air path supplies air drawn from the second storage chamber to the first region of the cooler,
The third air path has an air path formed in at least a portion of the partition wall and extending in the vertical direction, and the third air path has an air path formed in the partition wall that extends in the vertical direction, and the third air path has a second area having a lower cooling capacity than the first area of the cooler. supplying air sucked from the first storage chamber;
refrigerator. The cooler is a fin tube type cooler having a refrigerant pipe in which fins are arranged, and the second region has a higher installation density of the fins provided on the refrigerant pipe than the first region. is also low,
The refrigerator according to claim 1. The cooler has the refrigerant pipe in which a plurality of straight pipes and a plurality of U-shaped pipes arranged horizontally are connected alternately in a meandering manner, and the refrigerant pipe is arranged perpendicularly to the refrigerant pipe. A plurality of fins arranged along the straight tube are provided on the straight tube, and are arranged perpendicularly to the straight tube at the boundary between the straight tube and the U-shaped tube to extend the U-shaped tube. the cooler is supported by two side plates having surrounding holes;
a first opening of the third air passage to the cooler chamber faces a region between the side plate and a wall of the cooler chamber;
The refrigerator according to claim 2. There are two or more third air passages,
The first opening of the third air passage is located between one of the side plates and the wall of the cooler chamber and between the other side plate and the wall of the cooler chamber. facing both the area and
The refrigerator according to claim 3. The first opening of the third air path is formed at a position that overlaps the side plate in the height direction.
The refrigerator according to claim 3 or 4. The first openings of the two or more third air channels formed in the partition wall are spaced apart in the horizontal direction.
The refrigerator according to claim 4 or 5. The first region is an inner region sandwiched between the two side plates,
The second area is an area outside the two side plates,
The first opening of the third air path formed in the partition wall faces at least a part of the second area from the front, so that the air can pass through the third air path. supplying air to the second region;
Air from the second storage chamber is supplied from below to the cooler by the fourth air path, and the air supplied to the second area prevents the air from entering the second area. supplied to the first region,
The refrigerator according to claim 3. the first opening of the third air passage faces a lower end of the cooler;
The refrigerator according to claim 7. The jet pressure of the air supplied by the third air path is higher than the jet pressure of the air supplied by the fourth air path.
The refrigerator according to any one of claims 1 to 8. A second opening of the third air path to the first storage chamber is provided with a plurality of lattice members extending in the vertical direction and arranged in a horizontal direction.
The refrigerator according to any one of claims 1 to 9. A second opening of the third air path to the first storage chamber is provided with a guide member that guides air passing through the second opening,
The guide members extend horizontally and are provided in plurality at intervals in the vertical direction.
The refrigerator according to any one of claims 1 to 9. The guide member is arranged to be inclined upward toward the direction in which the cooler chamber is provided.
The refrigerator according to claim 11. When the partition wall partitions at least the cooler chamber and the first storage chamber into front and rear,
The partition wall is provided with an upper overhang that slopes downward toward the first storage chamber, and a lower overhang that slopes upward toward the first storage chamber,
The second opening of the third air path to the first storage chamber is defined above by the upper overhang and below by the lower overhang,
The amount of overhang of the lower overhang from the partition wall is larger than the amount of overhang of the upper overhang from the partition wall.
The refrigerator according to any one of claims 1 to 9. The third air path formed in the partition wall increases in height from the first storage chamber toward the direction in which the cooler chamber is provided.
The refrigerator according to any one of claims 1 to 13. a temperature information acquisition unit that acquires temperature information indicating the temperature of the second storage compartment;
a flap provided in the third air path;
a damper provided in the second air path;
a control unit that controls the flap and the damper based on the temperature information acquired by the temperature information acquisition unit;
The refrigerator according to any one of claims 1 to 14. when the damper is open, the flap is tilted to change the direction of air flow, and the air flowing into the cooler chamber from the third air path is caused to flow into an area of the cooler with relatively low cooling capacity;
The refrigerator according to claim 15. When the damper is closed, the flap is tilted to change the direction of air flow, and the air flowing into the cooler chamber from the third air path is caused to flow into a region of the cooler with a relatively high cooling capacity.
The refrigerator according to claim 15.