CN115560516A - Refrigerator with a door - Google Patents

Abstract

The invention provides a refrigerator, which does not need complex refrigeration circulation piping, restrains the reduction of energy-saving performance, restrains the generation of condensation and frost in a storage space, and is provided with a refrigerating chamber capable of storing under high humidity. The refrigerator is provided with: a low temperature chamber; a high temperature chamber having a higher temperature than the low temperature chamber; a cooler for supplying cold air to the low-temperature chamber; a heat transfer member having one surface facing the high temperature chamber side; and a heat transfer member cooling portion for cooling the heat transfer member by a refrigerant flowing through a refrigerant pipe of the cooler or by cold air cooled by the cooler, wherein the heat transfer member cooling portion includes a refrigerant pipe for flowing the refrigerant flowing through the cooler or an air passage for flowing the cold air cooled by the cooler, and when the heat transfer member cooling portion includes an air passage for flowing the cold air cooled by the cooler, the heat transfer member cooling portion can return the cold air flowing in the air passage to the cooler through a path not including the high-temperature chamber, and the heat transfer member is cooled by the cold air flowing in a second air passage having a smaller cross-sectional area of the air passage than that of the low-temperature chamber.

Description

Refrigerator with a door

Technical Field

The present invention relates to a refrigerator.

Background

As a background art in this field, japanese patent application laid-open No. 2020-180721 (patent document 1), for example, is known. The refrigerator described in patent document 1 includes a freezer compartment cooler, a refrigerating compartment and a freezer compartment, the refrigerating compartment is cooled by a direct cooling method using a cooling plate, and the freezer compartment is cooled by circulation of cold air that has exchanged heat with the freezer compartment cooler. In addition, the refrigerator is configured to be able to send cool air, which has been heat-exchanged with the freezer cooler, to the refrigerating room (fig. 1 of patent document 1). Patent document 1 discloses that cold air in a freezing chamber is transferred to a partition between a refrigerating chamber and a freezing chamber, the partition is used as a cooling plate, and a temperature compensating heater is provided on the cooling plate, so that when the cold air is too cold, the cold air is heated by the temperature compensating heater to maintain an appropriate temperature (fig. 10 of patent document 1).

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open No. 2020-180721

Disclosure of Invention

Problems to be solved by the invention

In the invention described in patent document 1, the configuration shown in fig. 1 can suppress the occurrence of condensation in the refrigerating chamber while suppressing the reduction in humidity of the refrigerating chamber. However, in the refrigerator described in patent document 1, piping for the refrigeration cycle needs to be arranged in the heat insulating wall, and complicated piping is required, which increases the component cost and the manufacturing cost. In the configuration described in fig. 10 of patent document 1, when a method is employed in which a partition wall between the freezing chamber and the refrigerating chamber is used as a cooling plate and heating is performed by a heater when the refrigerating chamber is too cold, energy saving performance is reduced due to the amount of electric power consumed for heating by the heater.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a refrigerator which does not require a complicated refrigeration cycle piping, suppresses a decrease in energy saving performance, suppresses dew condensation and frost generation in a storage space, and is provided with a refrigerating chamber capable of storing at high humidity.

Means for solving the problems

In order to solve the above problem, for example, the structure described in the claims is adopted. The present application includes a plurality of means for solving the above-described problems, and is a refrigerator including: a low temperature chamber; a high-temperature chamber having a temperature higher than that of the low-temperature chamber; a cooler for supplying cold air into the low-temperature chamber; a heat transfer member having one surface facing the high temperature chamber side; and a heat transfer member cooling portion for cooling the heat transfer member by circulating a refrigerant flowing through a refrigerant pipe of the cooler or by circulating cool air cooled by the cooler, wherein the heat transfer member cooling portion includes a refrigerant pipe for circulating the refrigerant flowing through the cooler or includes an air passage for circulating the cool air cooled by the cooler, and when the heat transfer member cooling portion includes an air passage for circulating the cool air cooled by the cooler, the heat transfer member cooling portion can return the cool air circulating in the air passage to the cooler through a path not including the high-temperature chamber, and the heat transfer member is cooled by cool air circulating in a second air passage having an air passage cross-sectional area smaller than that of the low-temperature chamber.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the present invention, it is possible to provide a refrigerator which does not require a complicated refrigeration cycle piping, suppresses a decrease in energy saving performance, suppresses dew condensation and frost generation in a storage space, and is provided with a refrigerating chamber capable of storing at high humidity.

Drawings

Fig. 1 is a front view of a refrigerator of embodiment 1.

Fig. 2 is a longitudinal sectional view of the refrigerator of embodiment 1.

Fig. 3 is a front view showing the structure inside the refrigerator of embodiment 1.

Fig. 4 is a schematic view illustrating an air path structure of the refrigerator according to embodiment 1.

Fig. 5 is an exploded perspective view showing a refrigerating compartment air duct of the refrigerator according to embodiment 1.

Fig. 6 is a structural view of a freezing cycle of the refrigerator of embodiment 1.

Fig. 7 is a view showing a refrigerating compartment damper of the refrigerator according to embodiment 1.

Fig. 8 is a longitudinal sectional view of the refrigerator of embodiment 2.

Fig. 9 is a schematic view showing an air path structure of the refrigerator according to embodiment 2.

Fig. 10 is a sectional view of the refrigerator of embodiment 3.

Fig. 11 is a structural view of a freezing cycle of the refrigerator of embodiment 3.

Fig. 12 is a perspective view of a first evaporator of the refrigerator of embodiment 3.

Fig. 13 is a side view of a second evaporator of the refrigerator of embodiment 3.

Fig. 14 is a perspective view of a cooling surface of a second evaporator of the refrigerator of embodiment 3.

Fig. 15 is a cross-sectional view of a heat transfer pipe of an evaporator of a refrigerator of example 3.

Fig. 16 is a front view of the arrangement of the components of the refrigeration cycle of the refrigerator according to example 3.

Fig. 17 is a structural view of a freezing cycle of the refrigerator of embodiment 4.

Fig. 18 is a front view of the arrangement of the components of the refrigeration cycle of the refrigerator according to example 4.

In the figure:

1-refrigerator, 2-refrigerating compartment (an example of high-temperature compartment), 3-ice-making compartment (an example of low-temperature compartment), 4-upper-stage freezing compartment (an example of low-temperature compartment), 5-lower-stage freezing compartment (an example of low-temperature compartment), 6-vegetable compartment, 8-cooler compartment, 9 a-freezing compartment fan, 9 b-refrigerating compartment fan, 10-heat-insulating box, 10 a-outer compartment, 10 b-inner compartment, 14-cooler, 24-compressor, 25-vacuum heat-insulating material, 27, 28-heat-insulating partition wall, 29, 30-partition, 31-control board, 39-mechanical compartment, 110-refrigerating compartment first air passage, 111-refrigerating compartment blow-out port, 115-refrigerating compartment first return air passage, 120-refrigerating compartment second air passage, 130-refrigerating compartment return air passage, 131-refrigerating compartment return air passage, 150-refrigerating compartment shutter (cold air cutting unit), 151-refrigerating compartment first shutter (first cold air cutting unit), 152-refrigerating compartment second shutter (second cold air cutting unit), 160-vegetable compartment shutter (vegetable heat transfer compartment shutter), 200-heat transfer member.

Detailed Description

The following are examples of the present invention.

[ example 1 ]

Embodiment 1 of a refrigerator according to the present invention will be described with reference to fig. 1 to 7.

Fig. 1 is a front view of the refrigerator of the present embodiment. As shown in fig. 1, the heat-insulated box 10 of the refrigerator 1 has storage compartments in the following order from above: the refrigerator comprises a refrigerating chamber 2, an ice making chamber 3, an upper-layer freezing chamber 4, a lower-layer freezing chamber 5 and a vegetable chamber 6 which are arranged side by side from left to right.

The refrigerator 1 includes doors for opening and closing openings of the storage compartments. These doors are rotary refrigerating chamber doors 2a and 2b divided left and right to open and close an opening of refrigerating chamber 2, and a pull-out type ice making chamber door 3a, upper freezing chamber door 4a, lower freezing chamber door 5a, and vegetable chamber door 6a to open and close openings of ice making chamber 3, upper freezing chamber 4, lower freezing chamber 5, and vegetable chamber 6, respectively. The interior material of these multiple doors is composed mainly of polyurethane foam. Each door includes a sealing member, not shown, on an outer peripheral portion of an inner surface thereof.

An operation portion 26 for performing an operation of setting the temperature in the cabinet is provided on the cabinet outer surface of the door 2a. The operation portion is provided on the outside of the door case, so that the user can perform operations such as temperature setting without opening the door.

Refrigerating room 2 is partitioned by heat insulating partition wall 27 and heat insulating partition wall 28 from ice making room 3 and upper freezing room 4, and from lower freezing room 5 to vegetable room 6, respectively. Further, partition 29 is provided at the following position in the front edge portion between ice making chamber 3 and upper-stage freezing chamber 4: and a position where the sealing member of the right end inner surface of the ice making chamber door 3a and the sealing member of the left end inner surface of the upper freezing chamber door 4a abut against each other in a state where the ice making chamber door 3a and the upper freezing chamber door 4a are closed. Partition 30 is provided at the following positions of the front edge between ice making compartment 3 and upper and lower freezing compartments 4: and a position where the sealing members of the lower end inner surfaces of the ice making chamber door 3a and the upper freezing chamber door 4a and the sealing member of the upper end inner surface of the lower freezing chamber door 5a abut against each other in a state where the ice making chamber door 3a, the upper freezing chamber door 4a, and the lower freezing chamber door 5a are closed.

Door hinges (not shown) for fixing the refrigerator 1 and the doors 2a and 2b are disposed in front of the top case outside of the heat-insulating box body 10 and at the front edge of the heat-insulating partition wall 27, and the door hinges at the upper part are covered with the door hinge covers 16.

Ice making chamber 3, upper-stage freezing chamber 4, and lower-stage freezing chamber are storage chambers whose interior is set to substantially freezing temperature (less than 0 ℃) and which are set to, for example, about-18 ℃ on average, refrigerating chamber 2 is a storage chamber whose interior is set to refrigerating temperature (0 ℃ or higher) and which is set to, for example, about 4 ℃ on average, and vegetable chamber 6 is a storage chamber whose interior is set to refrigerating temperature (0 ℃ or higher) and which is set to, for example, about 7 ℃ on average.

Fig. 2 isbase:Sub>A longitudinal sectional view (sectional viewbase:Sub>A-base:Sub>A in fig. 1) of the refrigerator of the present embodiment, and fig. 3 isbase:Sub>A front view ofbase:Sub>A state where the door and the container of fig. 1 are removed. Referring to fig. 2 and 3, the structure of the refrigerator 1 will be explained.

As shown in fig. 2, the refrigerator 1 is configured such that the outside and the inside of the refrigerator are partitioned by a heat insulating box 10, and the heat insulating box 10 is formed by filling a foamed heat insulating material (urethane foam in the refrigerator of the present embodiment) between an outer box 10a made of a steel plate and an inner box 10b made of a synthetic resin (e.g., ABS resin). In the heat insulating box body 10, a vacuum heat insulating material 25 having a lower thermal conductivity than the foamed heat insulating material is attached between the outer box 10a and the inner box 10b in addition to the foamed heat insulating material, thereby suppressing a decrease in the internal volume and improving the heat insulating performance. In this embodiment, the vacuum heat insulating material 25 is attached to the rear surface, the lower surface, the top shelf surface, and both side surfaces of the heat insulating box 10 and the lower freezing compartment door 5a, thereby improving the heat insulating performance of the refrigerator 1.

The heat insulating material inside the heat insulating partition wall 27 is expanded polystyrene, and the inside of the heat insulating partition wall 28 is filled with urethane foam. The urethane foam inside the heat-insulating partition wall 28 is filled together with the urethane foam of the heat-insulating box 10 in the step of foaming and filling urethane between the outer box 10a and the inner box 10b of the heat-insulating box 10.

The refrigerating compartment doors 2a, 2b include a plurality of door pockets 33a, 33b, 33c inside the compartment. In addition, the interior of the refrigerating compartment 2 is divided into a plurality of storage spaces by the shelves 34a, 34b, 34c, and 34 d. The ice making chamber door 3a, the upper freezing chamber door 4a, the lower freezing chamber door 5a, and the vegetable chamber door 6a are provided with an ice making chamber container 3b, an upper freezing chamber container 4b, a lower freezing chamber container 5b, and a vegetable chamber container 6b, respectively, which are integrally drawn out.

As shown in fig. 2 and 3, refrigerator 1 includes cooler chamber 8 in which cooler 14 is housed at the back of lower-stage freezing chamber 5, and freezing chamber fan 9a (second blower) at the upper part of cooler chamber 8. A freezer compartment air duct 100 is provided in the blowing region of freezer compartment fan 9 a. Freezing-room air duct 100 includes an ice-room outlet 101, an upper-stage freezing room outlet 102, and a lower-stage freezing room outlet 103, which blow out cold air to front ice-room 3, upper-stage freezing room 4, and lower-stage freezing room 5, respectively.

Further, refrigerator 1 includes freezer return air duct 105 through which return cold air from ice making compartment 3, upper-stage freezer compartment 4, and lower-stage freezer compartment 5 flows, at the lower front portion of cooler compartment 8. Freezer return air duct 105 is formed to have a width substantially equal to the width of cooler 14, and allows return cold air from ice making compartment 3, upper-stage freezer compartment 4, and lower-stage freezer compartment 5 to efficiently flow into cooler 14.

Further, refrigerator 1 includes vegetable compartment air passage 132 extending downward from the lower left portion of freezing compartment air passage 100 at the back of ice making compartment 3, upper-stage freezing compartment 4, and lower-stage freezing compartment 5, and vegetable compartment blow-out port 133 at the outlet of vegetable compartment air passage 132. Vegetable compartment return opening 136 is opened in the lower surface of heat insulating partition wall 28 between lower freezer compartment 5 and vegetable compartment 6, and vegetable compartment return air passage 135 extending from vegetable compartment return opening 136 to the lower front portion of cooler compartment 8 is provided in heat insulating partition wall 28.

The refrigerator 1 includes a refrigerating compartment first air passage 110 on the rear surface of the refrigerating compartment 2. The refrigerating compartment first air passage 110 includes refrigerating compartment blow-out ports 111a, 111b for blowing air into the refrigerating compartment 2 above the uppermost shelf 34a and between the uppermost shelf 34a and the second-tier shelf 34b from top to bottom. A refrigerating compartment second air passage 120 is provided behind the refrigerating compartment first air passage 110 and adjacent thereto with a partition wall interposed therebetween. The partition between the refrigerating compartment first air path 110 and the refrigerating compartment second air path 120 is formed of a heat transfer member 200, and air in the refrigerating compartment first air path 110 and air in the refrigerating compartment second air path 120 are heat-exchanged through the heat transfer member 200.

Here, the sectional area of refrigerating compartment second air passage 120 is smaller than the sectional areas in the horizontal direction and the vertical direction of the freezing temperature zone storage compartments such as ice making compartment 3, upper-stage freezer compartment 4, and lower-stage freezer compartment 5, and therefore the flow rate of the cold air flowing in refrigerating compartment second air passage 120 is higher than the flow rate of the cold air flowing in a large space in the storage compartment. Thus, according to the configuration of the present embodiment, unlike the case where the cooling is performed via the cold air in the adjacent freezing temperature zone, the refrigerating compartment second air passage 120 can be efficiently cooled.

The opening area of refrigerating room air outlet 111a is 1000mm ² The opening area of the refrigerating compartment air outlet 111b is 500mm ² The opening area of the air outlet opening to the storage space above the shelf 34a formed on the uppermost tier is larger than the opening area of the air outlet opening to the storage space above the shelf formed on the second tier or lower from the top (in the present embodiment, the shelf 34b on the second tier from the top). This makes it possible to supply more cold air to the storage space above refrigerating room 2, in which high-temperature air tends to collect due to natural convection in addition to heat intrusion from the outside of the cabinet, and thus to realize cooling with less temperature variation.

Further, refrigerator 1 includes refrigerating compartment first air passage return opening 115 on the inner side of the lower center of refrigerating compartment first air passage 110. The refrigerating chamber first duct return opening 115 is disposed above the shelf 34d defining the fresh ice chamber 36. Refrigerator 1 further includes refrigerating room return port 131 on the rear side of refrigerating room 2 and on the right side below shelf 34 d. Further, refrigerating room return air passage 130 is disposed at the rear right end of upper-stage freezer compartment 4 and lower-stage freezer compartment 5, and refrigerating room return air passage 130 is connected to the lower right portion of cooler compartment 8.

The refrigerator 1 includes a refrigerating compartment fan 9b (first blower) at a lower portion of the refrigerating compartment first air path 110. Further, a communication passage 140 communicating the refrigerating compartment first air passage 110 and the freezing compartment air passage 100 is provided in the back of the fresh air compartment 36. Further, a first cold air blocking plate 151 (first cold air blocking means) for blocking the flow of cold air from the freezing compartment air passage 100 into the communication passage 140 or the first refrigerating compartment air passage 110 is provided at an inlet portion (lower portion) of the communication passage 140. On the other hand, a refrigerating compartment second shutter 152 (second cold air cutting means) for cutting off the flow of cold air from the freezing compartment air path 100 into the refrigerating compartment second air path 120 is provided at an inlet portion (lower portion) of the refrigerating compartment second air path 120. The refrigerating chamber first barrier 151 and the refrigerating chamber second barrier 152 are barriers driven by a single motor. Hereinafter, a member having the functions of the refrigerating compartment first barrier 151 and the refrigerating compartment second barrier 152 combined is referred to as a refrigerating compartment barrier 150. Further, the details of the refrigerating compartment shutter 150 will be described later. Further, the vegetable compartment air passage 132 includes a vegetable compartment damper 160 as a cold air cutoff unit.

The refrigerator 1 includes a defrosting heater 21 below the cooler 14 in the cooler chamber 8, and a water conduit 23 on a lower surface of the cooler chamber 8. Further, a drain pipe 22 is provided from the lower end of the water conduit 23 to the machine room 39. The machine chamber 39 includes the compressor 24 and the evaporation pan 32 disposed above the compressor 24.

The defrosting heater 21 may be an electric heater of, for example, 50W to 200W, and in the present embodiment, is a radiation heater of 120W. The defrost water generated during defrosting of the cooler 14 is discharged from the water conduit 23 to the evaporation pan 32 above the compressor 24 through the water discharge pipe 22, and is evaporated by heat radiation from the compressor 24, ventilation by a machine room fan, not shown, and the like.

The refrigerator 1 includes a fresh ice compartment 36, the interior of which is maintained at about-1 ℃, in the refrigerating compartment 2 above the heat insulating partition wall 27, and the front of the fresh ice compartment 36 is openable and closable by a lid 36 a. The lid 36a has a gasket (not shown) on the outer periphery, and when the lid 36a is closed, the lid 36a and the outer frame 36b of the fresh food compartment 36 are in contact with each other via the gasket without a gap, and thus the lid 36a is sealed. A pump (not shown) for sucking air in the fresh air chamber 36 is provided on the back of the fresh air chamber 36, and the pressure in the fresh air chamber 36 is reduced to about 0.8 air pressure by driving the pump with the lid 36a closed. Accordingly, the inside of the fresh food compartment 36 is not directly blown with cold air by the lid 36a, and is reduced in pressure to become an environment in which the oxygen concentration is reduced, thereby forming a storage space in which drying and oxidation of food can be suppressed.

Refrigerator 1 includes refrigerating room temperature sensor 41, freezing room temperature sensor 43, and vegetable room temperature sensor 44 on the rear side of the inside of refrigerating room 2, upper-stage freezing room 4, lower-stage freezing room 5, and vegetable room 6, respectively, and includes cooler temperature sensor 40 on the top of cooler 14. The temperature of the refrigerating chamber 2, the ice-making chamber 3, the upper-stage freezing chamber 4, the lower-stage freezing chamber 5, the vegetable chamber 6, the cooler chamber 8, and the cooler 14 is detected by these sensors. In addition, the ice making compartment 3, the upper freezing compartment 4, and the lower freezing compartment 5 are integrated in the cabinet as a cooling space, and thus the temperature is detected by one freezing compartment temperature sensor 43. The refrigerator 1 includes an outside air temperature sensor 37 and an outside air humidity sensor 38 inside the door hinge cover 16 of the ceiling portion, and detects the temperature and humidity of the outside air (outside air). In addition, door sensors (not shown) are provided to detect the open/close states of the doors 2a, 2b, 3a, 4a, 5a, and 6a, respectively.

Fig. 4 is a schematic view showing an air duct structure for the flow of cold air in the refrigerator according to the present embodiment. As shown in fig. 4, in refrigerator 1, the cold air heat-exchanged with cooler 14 in cooler room 8 is boosted by freezer fan 9a and sent to freezer air passage 100. Cold air delivered to freezing chamber air duct 100 is blown out from ice making chamber outlet 101, upper-stage freezing chamber outlet 102, and lower-stage freezing chamber outlet 103 to ice making chamber 3, upper-stage freezing chamber 4, and lower-stage freezing chamber 5, respectively, regardless of the open/close states of refrigerating chamber first damper 151, refrigerating chamber second damper 152, and vegetable chamber damper 160. The cold air that has cooled ice making chamber 3, upper-stage freezing chamber 4, and lower-stage freezing chamber 5 cools each storage compartment, and returns from lower-stage freezing chamber 5 to cooler compartment 8 via freezing chamber return air duct 105.

When first refrigerating room damper 151 is in the open state, the cold air boosted by freezing room fan 9a is sent to ice making room 3, upper-stage freezing room 4, and lower-stage freezing room 5, flows from communication passage 140 to refrigerating room first air passage 110, and is sent from refrigerating room air outlet 111 to refrigerating room 2. The cold air having cooled the refrigerating room 2 flows through the refrigerating room return air passage 130 via the refrigerating room return opening 131, and returns to the cooler compartment 8. By opening refrigerating compartment first flap 151 in this manner, the low-temperature cold air having exchanged heat with cooler 14 is caused to flow directly into refrigerating compartment 2 from refrigerating compartment first air passage 110, and a quick-freeze operation mode is performed in which cooling of refrigerating compartment 2 is accelerated. In the quick-freeze operation mode, the freezing chamber fan 9a is driven, but the refrigerating chamber fan 9b may be driven or stopped.

When vegetable compartment shutter 160 is in the open state, the cold air that has been boosted in pressure by freezer fan 9a is sent to ice making compartment 3, upper-stage freezer compartment 4, and lower-stage freezer compartment 5, flows through vegetable compartment air duct 132 that branches downstream of freezer compartment air duct 100, and is blown out from vegetable compartment blow-out opening 133 into vegetable compartment 6. In the vegetable compartment 6, the air is blown out to the outside of the vegetable compartment container 6b, and the food such as vegetables stored in the vegetable compartment container 6b is prevented from drying and excessively lowering to a low temperature. The cold air that has cooled the vegetable compartment 6 flows through a vegetable compartment return air passage 135 (see fig. 2) provided in the heat insulating partition wall 28 via a vegetable compartment return opening 136 (see fig. 2) provided in the lower surface of the heat insulating partition wall 28, and returns to the cooler compartment 8.

When refrigerating room fan 9b is driven in a state where refrigerating room first flap 151 is closed and refrigerating room second flap 152 is open, an air flow is formed in which air in refrigerating room 2 enters refrigerating room first air passage 110 from refrigerating room first air passage return opening 115, flows through refrigerating room first air passage 110, reenters refrigerating room 2 from refrigerating room outlet opening 111, and circulates in refrigerating room 2. On the other hand, since the refrigerating compartment second shutter 152 is opened, the cold air raised in pressure by the freezing compartment fan 9a flows through the refrigerating compartment second air passage 120, exchanges heat with the air in the refrigerating compartment first air passage 110 at the heat transfer member 200, flows through the refrigerating compartment return air passage 130, returns to the cooler room 8, and exchanges heat with the cooler 14. In this way, the cooling operation mode is performed in which the air having exchanged heat with the cooler 14 is guided to the refrigerating compartment second air path 120 to cool the refrigerating compartment 2 while circulating the air from the refrigerating compartment first air path 110 through the refrigerating compartment 2 to reach the refrigerating compartment first air path 110 again without passing through the cooler 14.

Further, by driving the refrigerating room fan 9b in a state where the refrigerating room first damper 151 is closed and the refrigerating room second damper 152 is closed or the freezing room fan 9a is stopped, the following air flows are formed: air in refrigerating compartment 2 enters refrigerating compartment first air path 110 from refrigerating compartment first air path return opening 115, and again enters refrigerating compartment 2 from refrigerating compartment discharge opening 111 through refrigerating compartment first air path 110, and circulates in refrigerating compartment 2. On the other hand, since the refrigerating compartment second damper 152 is in the closed state or the freezing compartment fan 9a is in the stopped state, the low-temperature cold air having exchanged heat with the cooler 14 does not flow in the refrigerating compartment second air path 120, and the air in the refrigerating compartment first air path 110 is not cooled via the heat transfer member 200. In the state where the air supply to the refrigerating compartment second air passage 120 is stopped in this manner (the refrigerating compartment second damper 152 is closed or the freezing compartment fan 9a is stopped), the refrigerating compartment fan 9b is driven to perform a defrosting operation mode in which frost growing on the heat transfer member 200 is melted. The defrosting operation mode is performed until the heat transfer member reaches a temperature higher than 0 ℃, and the inside of the refrigerating compartment 2 is humidified by moisture contained in frost grown on the heat transfer member 200 as the frost melts. In the same control state as the defrosting operation mode, the driving time of refrigerating room fan 9b may be further shortened and fan power may be reduced by the moisturizing operation mode in which the operation is terminated when the temperature of heat transfer member 200 is 0 ℃.

Fig. 5 is an exploded perspective view illustrating the structures of the refrigerating compartment first air path 110 and the refrigerating compartment second air path 120. As shown in fig. 5, the refrigerating compartment first air path 110 and the refrigerating compartment second air path 120 formed in the rear portion of the refrigerating compartment 2 are configured by a first air path member 210, a second air path member 220, and a heat transfer member 200 provided between the first air path member 210 and the second air path member 220. First air-passage member 210 includes refrigerating room air outlets 111a and 111b on the front surface, and an opening 210a to which heat transfer member 200 is attached on the rear surface. The second duct member 220 has an opening 220a on the front surface thereof, and is integrally combined with the first duct member 210 to which the heat transfer member 200 is attached, thereby partitioning the refrigerating compartment first duct 110 and the refrigerating compartment second duct 120 via the heat transfer member 200. The second air passage member 220 includes a partition member 121 forming the forward flow path 120a and the return flow path 120b in the refrigerating compartment second air passage 120. Thus, when the refrigerating compartment second shutter 152 (see fig. 2, 3, or 4) is in the open state, the cold air flowing upward through the forward flow path 120a formed on the left side of the refrigerating compartment second air path 120 as indicated by the arrow inside the second air path member 220 is reversed in the upper portion of the refrigerating compartment second air path 120 and flows downward through the return flow path 120b on the right side of the refrigerating compartment second air path 120. As a result, the air in the refrigerating compartment second air path 120 efficiently exchanges heat with the air in the refrigerating compartment first air path 110 in a large area on the back of the refrigerating compartment 2. In the case of a refrigerator having a layout in which refrigerating room return opening 131 is formed on the left side, forward flow path 120a may be disposed on the right side and return flow path 120b may be disposed on the left side. In any case, by forming the forward flow path 120a and the return flow path 120b in the lateral direction, not only can a large area of the refrigerating compartment first air passage 110 facing the back be ensured to promote heat exchange, but also space saving in the front-rear direction can be achieved.

In the refrigerator 1 of the present embodiment, the first air path member 210 and the second air path member 220 are formed of synthetic resin (e.g., ABS resin), and the heat transfer member 200 is formed of aluminum, which is metal. By using a metal member having high thermal conductivity as the heat transfer member 200, the cold heat on the refrigerating compartment second air path 120 side is easily transferred to the air in the refrigerating compartment first air path 110, and thus the cooling via the heat transfer member 200 can be performed efficiently. As another example, the heat transfer member 200 may be formed of a resin (e.g., ABS resin). In this case, the heat transfer member 200 can be formed at a further reduced cost. That is, the heat transfer member 200 may be made of any material or shape as long as it has a function of transferring the cold and heat on the refrigerating compartment second duct 120 side to the air in the refrigerating compartment first duct 110. The first and second duct members 210 and 220 may be formed of any material, shape, or assembly, as long as the first and second refrigerating compartments 110 and 120 partitioned by the heat transfer member 200 can be formed. The heat transfer member 200 preferably does not have a structure generally divided by a heat insulating material, and preferably has an independent bubble structure and is not a member whose interior is depressurized. In this way, the second air passage 120, which is an example of the heat transfer member cooling portion, cools the heat transfer member 200.

Fig. 6 is a structural view of a freezing cycle of the refrigerator of the present embodiment. The refrigerator 1 of the present embodiment includes: a compressor 24; an out-tank radiator 50a (radiating means) for radiating heat from the refrigerant; wall heat dissipation pipes 50b (heat dissipation means disposed on the inner surface of the outer box 10a in the region between the outer box 10a and the inner box 10 b) disposed on the left and right side surfaces of the heat insulation box 10; dew condensation prevention piping 50c (heat radiation means disposed on the inner surfaces of the heat insulating walls 27, 28 and the partitions 29, 30) disposed on the front surfaces of the heat insulating walls 27, 28 and the partitions 29, 30 and configured to suppress dew condensation; a capillary tube 53 as a pressure reducing unit that reduces the pressure of the refrigerant; and a cooler 14 for absorbing heat in the tank by heat exchange between the refrigerant and air in the tank. The inner diameters of the wall surface heat radiation pipe 50b and the dew condensation prevention pipe 50c are 3.2mm, and the inner diameter of the capillary 53 is 0.7mm which is one third or less of the inner diameters of the wall surface heat radiation pipe 50b and the dew condensation prevention pipe 50c. Further, the refrigeration cycle is configured by providing a dryer 51 for removing moisture in the refrigeration cycle and a gas-liquid separator 54 for suppressing the inflow of the liquid refrigerant to the compressor 24, and connecting these components by a refrigerant pipe. The refrigerant pipe connecting the capillary tube 53, the cooler 14, and the compressor 24 includes a heat exchange portion 57 that exchanges heat of the refrigerant.

Next, the flow of the refrigerant in the refrigeration cycle of the refrigerator of the present embodiment will be described. In the refrigerator 1 of the present embodiment, when the compressor 24 is driven, the refrigerant is compressed to become a high-temperature high-pressure gas refrigerant, and enters the out-tank radiator 50a. The out-tank radiator 50a is a fin-and-tube heat exchanger. In the case-outside radiator 50a, the refrigerant is deprived of heat by ventilation by a case-outside fan not shown, has a reduced enthalpy, is in a two-phase state, and flows into the wall-surface heat radiation pipe 50b. The heat dissipation pipes 50b disposed on the wall surfaces of the heat insulating box 10 dissipate heat mainly from the refrigerant to the air outside the box through the outer wall of the heat insulating box 10. Then, the refrigerant enters the dew condensation prevention pipe 50c disposed on the front surface portions of the heat insulating partition walls 27, 28 and the partition portions 29, 30. Since the heat insulating partition walls 27 and 28 and the doors having heat insulating properties are provided in front of the partitions 29 and 30, the refrigerant mainly radiates heat to the air in the tank in the dew condensation prevention pipe 50c to become a liquid refrigerant, and reaches the capillary tube 53 after having been dehydrated by passing through the dryer 51.

The refrigerant is decompressed in the capillary tube 53, becomes a low-temperature low-pressure two-phase refrigerant, and reaches the inlet of the cooler 14. By driving freezing compartment fan 9a, the air returned from each storage chamber in the box passes through cooler 14, is cooled to a low temperature, and is cooled again in each storage chamber in the box. In this case, in refrigerating room 2 of the refrigerator according to the present embodiment, the cold heat of the cold air flowing through refrigerating room second air passage 120 is indirectly transferred to refrigerating room first air passage 110 via heat transfer member 200 to be cooled, and therefore, the cold heat is less likely to be supplied than in the case of directly conveying the cold air, and the cooling capacity is likely to be insufficient. Therefore, in the refrigerator of the present embodiment, the inner diameter of the capillary tube 53 is set to be equal to or less than one third of the inner diameters of the wall surface heat dissipation pipe 50b and the dew condensation prevention pipe 50c, and sufficient pressure reduction due to resistance is performed to lower the temperature of the cooler 14, and the temperature of the cold air supplied to the cold storage compartment second air passage 120 is set to be sufficiently low, whereby the cold storage compartment 2 can be cooled.

The refrigerant exchanges heat with the air in the tank in the cooler 14, increases in enthalpy, increases in dryness, becomes a substantially saturated gaseous refrigerant, and reaches the outlet of the cooler 14. A part of the pipe returning from the outlet of the cooler 14 to the compressor 24 is provided in proximity to the capillary tube 53 so as to exchange heat, and is heated by the refrigerant in the capillary tube to increase in enthalpy, where it is sucked into the compressor 24. By providing the heat exchange unit 57, the temperature of the refrigerant sucked into the compressor is increased, dew condensation and frost formation in the refrigerant pipe can be prevented, and the enthalpy of the refrigerant flowing into the cooler 14 is reduced by heat exchange, thereby improving the cooling capacity of the cooler 14. The refrigerant sealed in the refrigeration cycle is isobutane, which is a combustible refrigerant.

Fig. 7 is a diagram showing the structure of the refrigerating compartment shutter 150. The refrigerating compartment damper 150 includes openings 151a and 152a on the left and right of the motor housing 153. The opening 151a and the opening 152a are opened and closed by opening and closing plates 151b and 152 b. Specifically, the opening/ closing plates 151b and 152b are each controllable by a stepping motor (not shown) provided in the motor housing 153 in a range from a fully closed state with an open angle of 0 degrees to a fully open state with an open angle of 90 degrees. Among the functions of refrigerating compartment damper 150, the function of controlling the open/close state of opening 151a is defined as refrigerating compartment first damper 151, and the function of controlling the open/close state of opening 152a is defined as refrigerating compartment second damper 152. Thus, the refrigerating compartment barrier 150 is controlled by one motor for two barriers (a refrigerating compartment first barrier 151, a refrigerating compartment second barrier 152). This enables compact mounting and cost reduction.

In the machine room 39 at the lower portion of the back surface of the refrigerator 1, a control board (not shown) is disposed, which is a part of a control device, such as a CPU, a memory such as a ROM, and a RAM, and a control circuit. The control board is connected to an outside air temperature sensor 37, an outside air humidity sensor 38, a refrigerating room temperature sensor 41, a freezing room temperature sensor 43, a vegetable room temperature sensor 44, a cooler temperature sensor 40, and the like through electric wiring (not shown). ON the control board, ON/OFF of compressor 24, freezing room fan 9a, and refrigerating room fan 9b, rotation speed control, opening/closing control of refrigerating room first damper 151, refrigerating room second damper 152, and vegetable room damper 160, and control of the defrosting heater are performed based ON output values of the sensors, settings of operation unit 26, a program stored in advance in ROM, and the like.

The structure of the refrigerator of the present embodiment is described above, and effects exhibited by the refrigerator of the present embodiment will be described below.

The refrigerator of the present embodiment includes an ice making chamber 3 for cooling a freezing temperature zone, a cooler 14 for cooling an upper-stage freezing chamber 4 and a lower-stage freezing chamber 5, a first refrigerating chamber air passage 110 provided inside a refrigerating chamber 2, and a second refrigerating chamber air passage 120 which transports cold air heat-exchanged with the cooler 14 and is not communicated with the inside of the refrigerating chamber 2, and the first refrigerating chamber air passage 110 and the second refrigerating chamber air passage 120 are adjacent to each other via a heat transfer member 200 serving as a partition wall. Thereby becoming a refrigerator as follows: the refrigerator does not need complicated refrigeration circulation piping, suppresses the reduction of energy saving performance, suppresses the generation of dew condensation and frost in a storage space, and is provided with a refrigerating chamber for realizing the storage under high humidity. The reason will be described below while comparing with the conventional art.

As a conventional technique, for example, patent document 1 discloses a technique for generating a large amount of water vapor in a tank and causing dew condensation on a cooling plate provided in a refrigerating chamber when food having a large water content and a high temperature is put in the refrigerating chamber, and the like, in which: the refrigerator includes a freezer cooler for cooling a freezer compartment and a refrigerator compartment cooled by a direct cooling method using a cooling plate cooled by a second cooler separate from the freezer cooler, and sends cold air of a lower temperature and a lower humidity subjected to heat exchange with the freezer cooler to the refrigerator compartment, thereby reducing the humidity in the refrigerator compartment and suppressing dew condensation of the cooling plate. According to this conventional technique, when the temperature in the refrigerating chamber is high and the dew point temperature is higher than the temperature of the cooling plate, the low-temperature and low-humidity cold air that has exchanged heat with the freezer cooler is sent to the refrigerating chamber, the dew point temperature is lowered, and dew condensation on the cooling plate is suppressed. In this configuration, when the cooling panel temperature is sufficiently high and the refrigerating compartment cannot be cooled, it is necessary to frequently send low-humidity cold air to the refrigerating compartment, and the humidity of the refrigerating compartment cannot be kept high. In addition, in the embodiment in which the partition wall between the freezing chamber and the refrigerating chamber is used as the cooling plate, the temperature compensation heater is provided in the cooling plate in order to suppress a temperature decrease in the cooling plate, and the temperature decrease in the cooling plate is suppressed by heating the temperature compensation heater. In this configuration, the energy saving performance is reduced due to the amount of electricity consumed for heating of the temperature compensation heater. That is, the technique described in patent document 1 has the following problems: if the temperature of the cooling plate cannot be sufficiently increased, the humidity of the refrigerating chamber cannot be kept high, or the power consumption increases.

On the other hand, the refrigerator 1 of the present embodiment includes the refrigerating compartment first air passage 110 and the refrigerating compartment second air passage 120 which is not communicated with the inside of the refrigerating compartment 2 and which carries the cold air heat-exchanged with the cooler 14, and the refrigerating compartment first air passage 110 and the refrigerating compartment second air passage 120 are adjacent to each other via the heat transfer member 200 serving as the partition wall. Thus, the refrigerator 1 of the present embodiment can implement the following cooling operation modes: the air is circulated so as to pass through the refrigerating compartment 2 from the refrigerating compartment first air path 110 to the refrigerating compartment first air path 110 again without passing through the cooler 14, and the air heat-exchanged with the cooler 14 is guided to the refrigerating compartment second air path 120. By implementing this cooling operation mode, the freezing temperature zone chambers (ice making chamber 3, upper-stage freezing chamber 4, and lower-stage freezing chamber 5) are cooled inside refrigerating room 2, and therefore, the cold air having been subjected to heat exchange with cooler 14 and having a low temperature and a low humidity can be cooled indirectly via heat transfer member 200 to cool refrigerating room 2 without being sent to the inside of refrigerating room 2, and the humidity in refrigerating room 2 can be kept high. In addition, since the excessive moisture in the refrigerating compartment 2 basically forms frost and adheres to the heat transfer member 200 in the refrigerating compartment first air passage 110, it is possible to avoid the problem that dew condensation grows in the storage space in the refrigerating compartment 2 without using a heating means by a temperature compensating heater. Further, the heat transfer member 200 is cooled by the air in the refrigerating compartment second air path 120, and thus, a separate cooler for cooling the refrigerating compartment 2 is not required, and thus, an increase in manufacturing cost and component cost due to a complicated refrigerating cycle structure is suppressed.

In the refrigerator 1 of the present embodiment, the first air passage member 210 is disposed between the heat transfer member 200, which is cooled during cooling, and the refrigerating compartment 2 to form the air passage (refrigerating compartment first air passage 110), so that the heat transfer member 200 does not directly face the refrigerating compartment 2, which is a space for food. Therefore, even if frost or water (dew condensation water or defrosted water) is generated on the surface of heat transfer member 200, the frost or water does not directly contact with the food, so that the food is not easily fixed by the frost or wetted by water, and the refrigerator has high reliability. That is, by interposing the wall surface such as the air passage member between the storage chamber such as the refrigerating chamber 2 and the heat transfer member 200, it is possible to suppress frost and water generated in the heat transfer member 200 from reaching the storage chamber.

Further, the refrigerator 1 of the present embodiment includes a blower (refrigerating room fan 9 b) for generating an air flow in the refrigerating room first duct 110 and varying the amount of air blown. This allows the amount of heat exchange in the heat transfer member 200 in the first refrigerating compartment air passage 110 to be adjusted, and thus the temperature and humidity in the refrigerating compartment 2 can be maintained more finely.

Further, refrigerator 1 of the present embodiment includes a blower (freezing compartment fan 9 a) for generating an air flow in refrigerating compartment second air passage 120 and varying the amount of air blown. Accordingly, the amount of heat exchange in the heat transfer member 200 in the refrigerating compartment second air passage 120 can be adjusted, and thus the temperature and humidity in the refrigerating compartment 2 can be maintained more finely.

The refrigerator 1 of the present embodiment includes a communication passage 140 that communicates the freezing compartment air passage 100 and the refrigerating compartment first air passage 110 and guides air heat-exchanged in the cooler 14 to the refrigerating compartment first air passage 110, and the communication passage 140 includes a refrigerating compartment first damper 151. Accordingly, in the refrigerator 1 of the present embodiment, particularly when the heat load is large, the quick-freeze operation mode in which the cooling of the refrigerating compartment 2 is accelerated by opening the refrigerating compartment first damper 151 and allowing the low-temperature cold air having exchanged heat with the cooler 14 to flow directly into the refrigerating compartment 2 from the refrigerating compartment first air passage 110 can be performed, and quick cooling can be performed. In the implementation of the quick-freeze operation mode, the freezing chamber fan 9a is driven, but the refrigerating chamber fan 9b may be driven or stopped. In addition, the refrigerating compartment second shutter 152 in the implementation of the quick-freeze operation mode is preferably in the closed state, but may be in the open state.

In the refrigerator 1 of the present embodiment, when the frost growing on the heat transfer member 200 in the refrigerating compartment first air passage 110 is removed in the cooling operation mode or the quick-freeze operation mode, the defrosting operation mode is performed in which the refrigerating compartment fan 9b is driven in a state where the air supply to the refrigerating compartment second air passage 120 is stopped (a state where the refrigerating compartment second damper 152 is closed or a state where the freezing compartment fan 9a is stopped). In this defrosting operation mode, air passes through refrigerating compartment first air passage 110, passes through refrigerating compartment 2, and is recirculated to refrigerating compartment first air passage 110 without passing through cooler 14, similarly to the cooling operation mode, but unlike the cooling operation mode, air having exchanged heat with cooler 14 is not guided to refrigerating compartment second air passage 120, and therefore, the temperature of air circulating in refrigerating compartment first air passage 110 is higher than that in the cooling operation mode. As a result, frost on heat transfer member 200 can be melted by a heat load in refrigerating room 2 (heat flowing from outside to refrigerating room 2, etc.) without using a heater, and therefore energy saving performance is improved. In addition, the refrigerator compartment 2 can be highly humidified by the moisture contained in the frost grown on the heat transfer member 200, and thus the refrigerator compartment can have excellent moisture retention.

In the refrigerator 1 of the present embodiment, the refrigerating chamber first air path return opening 115 is disposed above the shelf 34d defining the fresh ice chamber 36. The fresh air chamber 36 is a storage space in which a lower temperature is maintained in the refrigerating chamber, and by adopting this configuration, the fresh air chamber 36 is less likely to be affected by the airflow in the refrigerating chamber 2 generated by the driving of the refrigerating chamber fan 9b, and therefore a lower temperature can be maintained more stably. Further, the cooling of the fresh air compartment 36 is mainly performed by cold heat transferred from the ice making compartment 3 and the upper freezing compartment 4 located therebelow.

[ example 2 ]

Next, embodiment 2 of the refrigerator according to the present invention will be described with reference to fig. 8 and 9. Fig. 8 is a longitudinal sectional view of the refrigerator according to embodiment 2, and fig. 9 is a schematic view showing an air passage structure of the refrigerator according to embodiment 2. Note that the same configuration as in embodiment 1 may not be described.

As shown in fig. 8, the refrigerator 1 of the present embodiment also includes a refrigerating compartment first air passage 110 on the rear surface of the refrigerating compartment 2. Above the uppermost shelf 34a of the first air passage 110 of the refrigerating compartment, the uppermost shelf 34a and the second shelf 34 from the top downThe spaces between b are provided with refrigerating room air outlets 111a and 111b for blowing air into refrigerating room 2, respectively. Opening area of refrigerating room air outlet 111a is 1000mm ² The opening area of the refrigerating compartment air outlet 111b is 500mm ² . Further, refrigerating compartment first duct return opening 115 is disposed above shelf 34d defining fresh ice compartment 36.

The refrigerating compartment second air passage 120 is provided behind the refrigerating compartment first air passage 110 and adjacent thereto with a partition wall interposed therebetween. A partition wall between the refrigerating compartment first air path 110 and the refrigerating compartment second air path 120 is formed of a heat transfer member 200, and air in the refrigerating compartment first air path 110 and air in the refrigerating compartment second air path 120 are heat-exchanged via the heat transfer member 200.

As shown in fig. 9, the refrigerator 1 of the present embodiment also includes a refrigerating compartment fan 9b in the refrigerating compartment first air path 110. Unlike embodiment 1, the refrigerator 1 of the present embodiment includes a communicating portion 170 communicating the refrigerating compartment first air passage 110 and the refrigerating compartment second air passage 120 at the back of the refrigerating compartment first air passage 110 above the uppermost shelf 34a, that is, downstream of the refrigerating compartment first air passage 110, and in the middle of the refrigerating compartment second air passage 120. Communication portion 170 includes a refrigerating compartment first flap 151 (cold air blocking unit) (see fig. 8), and controls the flow of cold air between refrigerating compartment second flow path 120 and refrigerating compartment first flow path 110 by opening and closing refrigerating compartment first flap 151. In this way, by disposing the refrigerating compartment first flap 151 above the uppermost shelf 34a, a large storage space can be secured for easy use because it is difficult for a user to reach the space and the space is not easy to use.

The refrigerating compartment second air path 120 includes a refrigerating compartment second damper 152. The refrigerating compartment second baffle 152 is disposed at the same position as the refrigerating compartment first baffle 151 or below the refrigerating compartment first baffle 151 in the refrigerating compartment second air passage 120, and in the refrigerator 1 of the present embodiment, is disposed at the outlet portion of the refrigerating compartment second air passage 120 and in the rear projection region of the heat insulating partition wall 27 (see fig. 8). In this embodiment, the second baffle 152 of the refrigerating chamber is disposed in the rear projection area of the heat insulating partition wall 27 which does not affect the food storage, thereby ensuring a large food storage space. In the present embodiment, the inlet of the refrigerating compartment second air passage 120 is not provided with a shutter and is always open, but a shutter may be disposed in the inlet. In addition, both of refrigerating compartment first flap 151 and refrigerating compartment second flap 152 may be disposed on the back of refrigerating compartment first air passage 110 above uppermost shelf 34a, and in this case, a flap driven by a single motor may be used, thereby achieving compact mounting and cost reduction.

Next, the flow of cold air is explained. When the refrigerating compartment first damper 151 is controlled to be in the closed state, the refrigerating compartment second damper 152 is controlled to be in the open state, the freezing compartment fan 9a is controlled to be in the driving state, and the refrigerating compartment fan 9b is controlled to be in the driving state while the compressor 24 is driven to supply the refrigerant to the cooler 14, the cold air boosted by the freezing compartment fan 9a is sent to the ice making compartment 3, the upper-stage freezing compartment 4, and the lower-stage freezing compartment 5, flows through the refrigerating compartment second air passage 120, exchanges heat with the air in the refrigerating compartment first air passage 110 via the heat transfer member 200, and flows through the refrigerating compartment return air passage 130 to return to the cooler compartment 8. On the other hand, the air in the first air passage of the refrigerating room, which has been brought into a low temperature by heat exchange with the cold air in the second air passage 120 of the refrigerating room via the heat transfer member 200, is blown out from the refrigerating room air outlets 111a and 111b by driving of the refrigerating room fan 9b, and cools the refrigerating room 2 (cooling operation mode). The cold air having cooled the refrigerating compartment 2 returns to the refrigerating compartment first air path 110 from the refrigerating compartment first air path return opening 115. By this operation, the low-temperature and low-humidity cold air having exchanged heat with cooler 14 can be cooled by indirect cooling via heat transfer member 200 without being sent to the inside of refrigerating compartment 2, and the inside of refrigerating compartment 2 can be kept at high humidity. In addition, since the excessive moisture in the refrigerating compartment 2 basically forms frost and adheres to the heat transfer member 200 in the refrigerating compartment first air passage 110, it is possible to avoid a problem that dew condensation grows in the storage space in the refrigerating compartment 2 without using a unit for heating by a temperature compensation heater. Further, the heat transfer member 200 is cooled by the air in the refrigerating compartment second air path 120, and an additional cooler for cooling the refrigerating compartment 2 is not required, thereby suppressing an increase in manufacturing cost and component cost associated with the use of a complicated refrigerating cycle structure.

When refrigerating room first damper 151 is closed, refrigerating room second damper 152 is closed, or refrigerating room fan 9b is driven with freezing room fan 9a stopped, the supply of cold air into refrigerating room second air path 120 is stopped, and heat transfer member 200 is not cooled. On the other hand, the refrigerating compartment fan 9b is driven to generate an air flow flowing through the refrigerating compartment first air passage 110. By this airflow, frost generated in heat transfer member 200 by the cooling operation is melted by the heat load in refrigerating room 2 (heat flowing from the outside of the refrigerator into refrigerating room 2, etc.), and therefore defrosting (defrosting operation mode) can be performed without using a heater, and energy saving performance is improved. Furthermore, the moisture contained in the frost grown on the heat transfer member 200 can humidify the interior of the refrigerating compartment 2 to provide a refrigerating compartment with excellent moisture retention.

When the refrigerating chamber first damper 151 is controlled to be in the open state, the refrigerating chamber second damper 152 is controlled to be in the closed state, the freezing chamber fan 9a is controlled to be in the drive state, and the refrigerating chamber fan 9b is controlled to be in the stop state in a state where the compressor 24 is driven and the refrigerant is supplied to the cooler 14, the cold air boosted by the freezing chamber fan 9a is sent to the ice making chamber 3, the upper-stage freezing chamber 4, and the lower-stage freezing chamber 5, flows in an upstream portion of the refrigerating chamber second air passage 120, enters the refrigerating chamber first air passage 110 through the open refrigerating chamber first damper 151, is blown out to the refrigerating chamber 2 from the refrigerating chamber blow-out ports 111a, 111b, and a part of the cold air flows into the refrigerating chamber 2 from the refrigerating chamber first air passage return port 115. The cold air having cooled the refrigerating compartment 2 flows through the refrigerating compartment return air passage 130 via the refrigerating compartment return opening 131, and returns to the cooler compartment 8. With this operation, particularly when the heat load is large, the low-temperature cold air having exchanged heat with cooler 14 can be directly sent into refrigerating room 2 without consuming power for driving refrigerating room fan 9b, and therefore, the cooling of refrigerating room 2 can be accelerated while suppressing energy consumption (first rapid freezing operation mode).

In a state where the compressor 24 is driven to supply the refrigerant to the cooler 14, when the refrigerating chamber first shutter 151 is controlled to be open and closed, the refrigerating chamber second shutter 152 is controlled to be closed, the freezing chamber fan 9a is controlled to be driven, and the refrigerating chamber fan 9b is controlled to be driven, the cold air boosted by the freezing chamber fan 9a is sent to the ice making chamber 3, the upper-stage freezing chamber 4, and the lower-stage freezing chamber 5, flows through the upstream portion of the refrigerating chamber second air passage 120, enters the refrigerating chamber first air passage 110 via the opened refrigerating chamber first shutter 151, and is mainly blown out to the refrigerating chamber 2 from the refrigerating chamber outlet 111a having a large opening area. The cold air in refrigerating room 2 flows from refrigerating room first duct return opening 115 into refrigerating room first duct 110 by driving of refrigerating room fan 9b, is blown out from refrigerating room blow-out openings 111a and 111b, and partially flows into refrigerating room return duct 130 through refrigerating room return opening 131 to return to cooler compartment 8. By this operation, the air in the refrigerating chamber can be stirred while the low-temperature cold air having exchanged heat with the cooler 14 is directly sent into the refrigerating chamber 2, and temperature variation can be suppressed (second-speed freezing operation mode).

In the present embodiment, the refrigerating room fan 9b is set to a height facing the refrigerating room first air path return opening 115, but the refrigerating room fan 9b may be set to a height above the refrigerating room first air path return opening 115. This can prevent the cold air that has flowed into the refrigerating compartment first flow path 110 through the communication portion 170 from being blown out into the refrigerating compartment 2 from the refrigerating compartment first flow path return opening 115 when the refrigerating compartment first flap 151 is in the open state and the refrigerating compartment fan 9b is in the stopped state. Further, by setting the height of the center of gravity of the refrigerating room fan 9b to be higher than the refrigerating room air outlet 111b, particularly, to be higher than the uppermost shelf 34a, the rear upper portion of the uppermost shelf 34a which is difficult to reach by the hand of the user can be effectively used as the installation space of the refrigerating room fan 9b.

The closed state of the refrigerating compartment first damper 151 and the refrigerating compartment second damper 152 is not limited to a state in which the flow path is completely shut off, and includes a state in which a slight gap is opened (for example, a state in which the flow rate is 10% or less compared to the opened state).

[ example 3 ] A method for producing a polycarbonate

A refrigerator 1 according to embodiment 3 of the present invention will be described with reference to fig. 10 to 16.

Fig. 10 is a sectional view of the refrigerator of embodiment 3. First evaporator 301a (freezing evaporator) is provided on the back surface side of lower freezer compartment 5, and cools ice making compartment 3, upper freezer compartment 4, and lower freezer compartment 5, which are freezing temperature zone compartments, and also cools vegetable compartment 6, which is a refrigerating temperature zone compartment, and, if necessary, refrigerating compartment 2. The freezing chamber fan 9a provided above the first evaporator 301a sends the cold air heat-exchanged with the first evaporator 301a to the refrigerating chamber 2, the ice-making chamber 3, the upper freezing chamber 4, the lower freezing chamber 5, and the vegetable chamber 6 via the refrigerating chamber air passage 300, the freezing chamber air passage 100, and the vegetable chamber air passage (not shown). In this embodiment, the freezing chamber fan 9a is in the form of a propeller fan, and efficiently delivers cold air in the axial direction. Hereinafter, ice making chamber 3, upper-stage freezing chamber 4, and lower-stage freezing chamber 5 may be collectively referred to as a freezing temperature zone chamber.

The cold air to be sent to refrigerating room 2 is controlled by opening and closing refrigerating room damper 306. The refrigerating compartment damper 306 includes a baffle 307, and the opening/closing angle of the baffle 307 is adjusted by motor driving to adjust the air flow rate. The air delivered to the refrigerating compartment 2 is returned to below the first evaporator 301a, so that it can be continuously cooled. Further, since second evaporator 301b is provided in refrigerating room 2, refrigerating room damper 306 is opened to promote cooling of refrigerating room 2 when a large heat load cannot maintain cooling of refrigerating room 2 by second evaporator 301b.

The cold air is sent to the vegetable compartment 6 by opening and closing a vegetable compartment shutter (not shown). The vegetable compartment damper is provided with a baffle plate (not shown), and the opening and closing angle of the baffle plate is adjusted by driving a motor to adjust the amount of air blown. The air delivered to the vegetable compartment 6 is returned to the lower side of the first evaporator 301a, thereby enabling continuous cooling.

A defrosting heater 21 is provided below the first evaporator 301 a. When frost grows on the surface of the first evaporator 301a and the air passage is narrowed, the defrosting heater 21 is operated to defrost the air passage.

Second evaporator 301b (a refrigerating evaporator) is provided on the back side of refrigerating room 2, and cools refrigerating room 2 as a refrigerating temperature zone chamber. Refrigerating room fan 9b provided below second evaporator 301b sends the cold air heat-exchanged with second evaporator 301b to refrigerating room 2 via refrigerating room air trunk 300. In the present embodiment, the refrigerating chamber fan 9b is in the form of a centrifugal fan, and effectively conveys cold air in the circumferential direction (so long as it is directed upward).

Here, the cold air having exchanged heat with the first evaporator 301a basically cools the freezing temperature zone chamber, and thus has a low temperature and a low humidity as the temperature is lowered. However, in the refrigerating compartment 2 of the present embodiment, the second evaporator 301b cools the compartment without a large heat load. That is, since the low-humidity cold air having exchanged heat with first evaporator 301a does not directly flow into refrigerating room 2, refrigerating room 2 can be kept in a high-humidity state.

By operating refrigerating room fan 9b without circulating the refrigerant in second evaporator 301b, the frost growing on cooling surface 304 of second evaporator 301b can be removed without using a heating source such as a heater. In addition, since the air sent to refrigerating room 2 during the defrosting operation of second evaporator 301b is about 0 ℃ (frost temperature), refrigerating room 2 can be cooled while defrosting. That is, in the present embodiment, since the defrosting operation and the cooling operation of refrigerating room 2 are simultaneously performed while compressor 24 is stopped, power consumption is lower than that in general defrosting using a heating source such as a heater. Therefore, even when the defrosting operation of the refrigerating chamber 2 is frequently performed, it is possible to prevent the energy saving type from being damaged. Further, since refrigerating room 2 can be cooled even in a state where compressor 24 is stopped, unstable temperature fluctuation in refrigerating room 2 can be suppressed, and a temperature range of, for example, 0 to 2 degrees can be controlled. In addition, the refrigerating chamber 2 can be highly humidified by the frost melted. Hereinafter, the operation of defrosting and cooling the refrigerating compartment 2 by operating the refrigerating compartment fan 9b with the compressor 24 stopped is referred to as off-cycle operation.

Control board 31 is disposed ON the back side of the upper wall of refrigerator 1, and ON/OFF, control of the number of rotations, and open/close control of refrigerating compartment shutter 306 of compressor 24, freezing compartment fan 9a, and refrigerating compartment fan 9b are performed in accordance with control means stored in control board 31.

In the machine chamber 39 provided below the refrigerator 1, a first heat sink 308a (not shown in fig. 10) and an outside-cabinet blower 309 (not shown in fig. 10) are disposed in addition to the compressor 24.

Fig. 11 is a structural view of a freezing cycle of the refrigerator of embodiment 3. As shown in fig. 11, the refrigerator 1 of the present embodiment includes: a compressor 24 that compresses a refrigerant; a first radiator 308a and a second radiator 308b as heat radiation means for radiating heat from the refrigerant; a capillary tube 53 as a pressure reducing unit that reduces the pressure of the refrigerant; and a first evaporator 301a and a second evaporator 301b for absorbing heat in the tank by exchanging heat between the refrigerant and the air in the tank. The refrigerator 1 further includes a dryer 51 for removing moisture in the refrigeration cycle and a gas-liquid separator 54 for preventing a liquid refrigerant from flowing into the compressor 24, and the two are connected by a refrigerant pipe 302 to constitute the refrigeration cycle.

The first radiator 308a has a structure in which the heat radiation efficiency is higher than that of the second radiator 308b because the air outside the tank is sucked by the outside-tank blower 309. In addition, isobutane is used as the refrigerant of the refrigerator 1 of the present embodiment. The compressor 24 of the present embodiment includes an inverter, and is capable of changing the rotation speed. In the refrigeration cycle shown in fig. 11, a capillary tube is used as an example of the pressure reducing means, but an expansion valve or a combination of an expansion valve and a capillary tube may be used.

Fig. 12 is a perspective view of a first evaporator of the refrigerator of embodiment 3. As shown in fig. 12, the first evaporator 301a is a cross-fin tube heat exchanger, and a heat transfer tube 303 bent a plurality of times penetrates a plurality of aluminum fins 305. Further, a gas-liquid separator 54 is provided on the refrigerant outlet side of the heat transfer pipe 303. The first evaporator 301a is disposed in a space between the inner box 10b and the freezing temperature zone chamber.

Fig. 13 is a side view of a second evaporator of the refrigerator of embodiment 3. As shown in fig. 13, the second evaporator 301b is composed of heat transfer tubes 303 and a cooling surface 304, and the heat transfer tubes 303 of the second evaporator 301b are attached to the inside of the wall surface of the heat insulation box 10. The heat transfer pipe 303 is bent a plurality of times, is disposed in the foamed heat insulating material between the outer box 10a and the inner box 10b, and is in contact with the back surface side of the inner box 10 b. Further, cooling surface 304 is fixed to refrigerating room 2 side of inner box 10b with an adhesive or the like, and heat transfer pipe 303 cools refrigerating room 2 via cooling surface 304. By mounting the heat transfer tubes 303 of the second evaporator 301b inside the wall surface of the heat insulating box 10 in this way, the cooling system can be made smaller and the food storage volume can be increased. Further, a vacuum heat insulating material 25 is provided on the rear surface of the second evaporator 301b, and heat absorption from the outside of the tank is suppressed.

Fig. 14 is a perspective view of a cooling surface of a second evaporator of the refrigerator of embodiment 3. As shown in fig. 14, since fins 305 are provided on cooling surface 304, the heat transfer area is increased, and the cooling efficiency of refrigerating compartment 2 is improved, thereby improving the energy saving performance of refrigerator 1. Since the fins 305 are formed parallel to the flow of the cold air, an increase in air passage resistance can be suppressed. Further, since the material of the fins 305 is resin, the cooling surface temperature is higher than that in the case where the material of the fins 305 is metal, the amount of frost formation in the second evaporator 301b can be suppressed, and the off-cycle operation time can be shortened. Further, by suppressing the amount of frost formation, dehumidification of refrigerating room 2 can be suppressed, and refrigerating room 2 can be kept at high humidity. In addition, the risk of freezing of the refrigerated food can be reduced by increasing the cold air temperature. For the same reason, the cooling surface 304 is also preferably made of resin. However, the heat conductivity of the cooling surface 304 and the fins 305 is higher than that of the inner case 10 b. In the present embodiment, cooling surface 304 and fins 305 are made of resin in order to suppress the amount of frost formation, but when the cooling performance of refrigerating room 2 is prioritized, they may be made of metal such as aluminum.

As described above with reference to fig. 13 and 14, the first evaporator 301a has a cross fin tube type structure that facilitates improvement in cooling efficiency, and the second evaporator 301b has a heat transfer tube 303 attached to the inside of the wall surface of the heat insulating box 10 to suppress frost growth, and has a cooling surface 304 or the like made of a resin material having low thermal conductivity. That is, on the first evaporator 301a side, the temperature difference between the air and the refrigerant is small (about 5 ℃), and the frost growth rate is slow, so the improvement of cooling is prioritized over the suppression of frost growth. On the other hand, on the second evaporator 301b side, since the temperature difference between the air and the refrigerant is large (about 25 ℃), and the frost growth rate is high, the frost growth is suppressed more preferentially than the cooling efficiency. In this way, the energy saving performance of the refrigerator 1 can be improved by taking into consideration the characteristics of the respective evaporators.

Fig. 15 is a sectional view of a heat transfer pipe of an evaporator of a refrigerator according to example 3, a showing a sectional view of a heat transfer pipe of a first evaporator 301a, and b showing a sectional view of a heat transfer pipe of a second evaporator 301b. As shown in fig. 15, the heat transfer tubes 303 of the first evaporator 301a have grooves on the inner surface thereof, and the heat transfer area on the refrigerant side is increased, so that the temperature of the heat transfer tubes 303 is as close as possible to the refrigerant temperature, thereby improving the cooling efficiency. On the other hand, the inner surface of the heat transfer pipe 303 of the second evaporator 301b is smooth, and the temperature of the heat transfer pipe 303 is higher than the refrigerant temperature, thereby suppressing the amount of frost formation and shortening the defrosting time. In this way, on the first evaporator 301a side, since the temperature difference between the air and the refrigerant is small (about 5 ℃), and the frost growth rate is slow, the temperature difference between the refrigerant and the heat transfer pipe 303 is minimized, and the cooling efficiency is easily improved. On the other hand, on the second evaporator 301b side, the temperature difference between the air and the refrigerant is increased (about 25 ℃), and the frost growth rate is increased, so that the temperature difference between the refrigerant and the heat transfer tubes 303 is increased as much as possible, and the frost growth is suppressed.

Fig. 16 is a front view of the arrangement of the components of the refrigeration cycle of the refrigerator according to example 3. As shown in fig. 16, the compressor 24 and the first heat sink 308a are provided in the machine chamber 39, the second heat sink 308b is provided in the side surface of the refrigerator 1, the first evaporator 301a is provided in (the back surface side of) the freezing temperature zone chamber, and the second evaporator 301b is provided in (the back surface side of) the refrigerating chamber 2. Further, the refrigerant pipe 302 connecting the second evaporator 301b and the first evaporator 301a is disposed so as to extend downward from the second evaporator 301b. Further, the heat transfer pipe 303 of the second evaporator 301b is configured to monotonically decrease.

Here, it is assumed that the liquid refrigerant flows through the heat transfer tubes 303 of the second evaporator 301b from the vertically upper side to the vertically lower side during driving of the compressor 24, and this is expressed as a monotonous "downward" movement of the heat transfer tubes 303. However, when the liquid refrigerant flows through the heat transfer tubes 303 of the second evaporator 301b from the vertically downward direction to the vertically upward direction during driving of the compressor 24, the heat transfer tubes 303 may be interpreted as being monotonously "raised". In any case, the heat transfer pipe 303 of the second evaporator 301b may be continuously inclined so that the liquid refrigerant in the heat transfer pipe 303 continuously descends due to gravity while the compressor 24 is stopped. Thus, even with a slight local level or increased inclination, as long as the liquid refrigerant is drained by gravity, it is allowed.

Thus, in the off cycle operation, the liquid refrigerant in the second evaporator 301b is reduced by gravity, so that the heat load for melting frost is reduced, and the defrosting efficiency of the refrigerating room 2 (the efficiency of the off cycle operation) can be improved. Further, since the frost in the second evaporator 301b is melted and the air containing moisture is supplied to the refrigerating room 2, the refrigerating room 2 can be humidified to a high degree, and the freshness of the refrigerated food can be improved.

As shown in fig. 16, the second evaporator 301b is provided above the first evaporator 301a, and thereby the flow of the liquid refrigerant from the first evaporator 301a to the second evaporator 301b in the off-cycle operation is suppressed, and the increase in the heat load is suppressed, and the defrosting efficiency (the efficiency of the off-cycle operation) is improved. In the present embodiment, since the second evaporator 301b and the first evaporator 301a are connected in series by the refrigerant pipe 302 extending downward from the second evaporator 301b, the first evaporator 301a functions as a tank (storage unit) that stores the liquid refrigerant flowing down from the second evaporator 301b. Therefore, the liquid refrigerant is reliably discharged from the heat transfer tubes 303 of the second evaporator 301b, and as a result, the defrosting efficiency is further improved. The tank for storing the liquid refrigerant may be a header or the like provided separately from the first evaporator 301a, for example, at a position lower than the second evaporator 301b, as long as it is a member having a larger cross-sectional area than the heat transfer tubes 303.

In the present embodiment, not only the first evaporator 301a but also the second evaporator 301b is provided in the refrigerating compartment 2. Accordingly, as compared with the case where only the first evaporator 301a is installed, the amount of frost formation of the first evaporator 301a can be reduced, the defrosting operation time of the freezing temperature zone can be reduced, and the energy saving performance of the refrigerator 1 can be improved. In the present embodiment, the frost is grown in the second evaporator 301b and melted by the off-cycle operation, and therefore, compared with the increase in power consumption due to the off-cycle operation, shortening of the defrosting time of the freezing temperature zone chamber has a greater effect, and the power consumption of the refrigerator 1 can be further reduced.

Further, by connecting the first evaporator 301a and the second evaporator 301b in series as in the present embodiment, the number of capillaries 53 is reduced from two to one as compared with the case of connecting them in parallel, and members such as a valve for branching the refrigerant flow path and a check valve for suppressing the backflow of the refrigerant are not required. As a result, the refrigerator 1 can be manufactured at low cost, and the rate of manufacturing defects can be reduced because the refrigeration cycle structure is simple. In the present embodiment, the refrigerant passes through the second evaporator 301b, then passes through the first evaporator 301a and the gas-liquid separator 54, and the gas-liquid separator 54 is attached to the inside of the freezing compartment air passage 100. With this configuration, since it is not necessary to mount the gas-liquid separator 54 inside the wall surface of the heat insulating box 10, it is possible to achieve both reduction in thickness of the heat insulating box 10 and improvement in defrosting efficiency.

Similarly, by setting the refrigerant upstream side as the second evaporator 301b and the refrigerant downstream side as the first evaporator 301a, the refrigerant temperature of the first evaporator 301a is reduced by the pressure loss in the heat transfer pipe as compared with the second evaporator 301b. Further, since the amount of the liquid refrigerant on the refrigerant downstream side is smaller (the dryness is higher), the heat transfer rate on the refrigerant side is improved. Therefore, the first evaporator 301a is configured to increase the temperature difference between the air and the refrigerant as much as possible, thereby facilitating improvement of the cooling efficiency, and the second evaporator 301b is configured to reduce the temperature difference between the air and the refrigerant as much as possible, thereby facilitating suppression of the growth of frost.

[ example 4 ] A method for producing a polycarbonate

Next, a refrigerator 1 according to embodiment 4 of the present invention will be described with reference to fig. 17 and 18. The storage chamber of the refrigerator 1 of embodiment 4 is only a refrigerating chamber, and is configured to be cooled by one evaporator 301 c. Other structures are the same, and redundant description is omitted.

Fig. 17 is a structural view of a freezing cycle of the refrigerator of embodiment 4. As shown in fig. 17, the refrigerator 1 of the present embodiment includes a compressor 24, a first radiator 308a and a second radiator 308b as heat radiating means for radiating heat of refrigerant, a capillary tube 53 as pressure reducing means for reducing the pressure of refrigerant, and an evaporator 301c (refrigerating evaporator) for absorbing heat in the refrigerator by exchanging heat between the refrigerant and air in the refrigerator. The refrigerator 1 further includes a dryer 51 for removing moisture in the refrigeration cycle, and the refrigeration cycle is configured by connecting these components by a refrigerant pipe 302.

Fig. 18 is a front view of the arrangement of the components of the refrigeration cycle of the refrigerator according to example 4. As shown in fig. 18, the compressor 24 and the first heat sink 308a are provided in the machine chamber 39, the second heat sink is provided in the side surface of the refrigerator 1, and the evaporator 301c is provided in (the rear surface side of) the refrigerating chamber 2. The heat transfer pipe 303 of the evaporator 301c is configured to monotonically decrease, and the refrigerant pipe connecting the evaporator 301c and the compressor 24 is disposed so as to extend downward from the evaporator 301 c. Therefore, as in example 3, in the off-cycle operation, the liquid refrigerant in the evaporator 301c is reduced by gravity, and therefore the heat load for melting frost is reduced, and the defrosting efficiency of the refrigerating compartment 2 can be improved. Further, since the frost in evaporator 301c is melted and air containing moisture is supplied to refrigerating room 2, refrigerating room 2 is humidified to a high degree, and the freshness of the refrigerated food can be improved. In the present embodiment, the compressor 24 functions as a tank (storage portion) that stores the liquid refrigerant flowing down from the evaporator 301c, and the liquid refrigerant is reliably discharged from the heat transfer tubes 303 of the evaporator 301c, thereby further improving the defrosting efficiency.

The present invention is not limited to the above-described embodiments, but includes various modifications. For example, the above-described embodiments are examples described in detail to explain the present invention easily and understandably, and are not limited to having all the configurations described. In addition, as for a part of the configuration of the embodiment, addition, deletion, and replacement of other configurations may be performed.

Claims (11)

1. A refrigerator is characterized in that a refrigerator body is provided with a refrigerator door,

the disclosed device is provided with: a low temperature chamber; a high-temperature chamber having a temperature higher than that of the low-temperature chamber; a cooler for supplying cold air to the low-temperature chamber; a heat transfer member having one surface facing the high temperature chamber side; and a heat transfer member cooling unit for cooling the heat transfer member by a refrigerant flowing through a refrigerant pipe of the cooler or by cold air cooled by the cooler,

the heat transfer member cooling portion includes a refrigerant pipe through which a refrigerant flowing through the cooler flows, or an air passage through which cool air cooled by the cooler flows,

the heat transfer member cooling portion, when including an air passage through which cool air cooled by the cooler flows, can return cool air flowing through the air passage to the cooler through a path not including the high-temperature chamber,

the heat transfer member is cooled by cool air flowing through a second duct having a duct cross-sectional area smaller than that of the low-temperature chamber.

2. The refrigerator according to claim 1,

the disclosed device is provided with: a first air passage for allowing air to flow from a storage compartment as a refrigerating temperature zone of the high-temperature compartment; and a second air passage which circulates the air heat-exchanged with the cooler and is not communicated with the refrigerating temperature zone storage chamber,

the first air passage and the second air passage are adjacent to each other with a partition wall interposed therebetween.

3. The refrigerator according to claim 2,

the refrigerator further includes a first blower that generates an air flow that passes through the cold storage temperature zone storage compartment from the first air passage and returns to the first air passage without passing through the cooler.

4. The refrigerator according to claim 3,

the disclosed device is provided with: a communication passage that guides the air heat-exchanged with the cooler to the first air passage; and a first cold air blocking unit provided in the communication passage and blocking an air flow flowing from the cooler to the first air passage,

when the first cold air cutoff unit is in the open state, the air heat-exchanged with the cooler flows into the cold storage temperature zone storage chamber through the first air passage.

5. The refrigerator according to claim 2,

a second blower for generating an air flow for guiding the air heat-exchanged with the cooler to a storage room of a freezing temperature zone as the low temperature room,

the second blower also generates an air flow for guiding the air heat-exchanged with the cooler to the second air passage.

6. The refrigerator according to claim 5,

and a second cold air cutting unit for cutting off the airflow flowing from the cooler into the second air passage.

7. The refrigerator according to claim 5,

the first air passage is formed at the back of the refrigerating temperature zone storage chamber,

the second air passage has a forward flow passage and a return flow passage facing a back portion of the first air passage, and the forward flow passage and the return flow passage are arranged side by side in a left-right direction.

8. The refrigerator according to claim 2, characterized by having the following operation modes:

an operation mode in which air is circulated from the first air passage to the first air passage through the cold storage temperature zone storage compartment without passing through the cooler, and air heat-exchanged with the cooler is guided to the second air passage;

an operation mode in which air is circulated from the first air passage to the first air passage through the cold storage temperature range storage compartment without passing through the cooler, and air heat-exchanged with the cooler is not guided to the second air passage; and

and an operation mode in which the air heat-exchanged with the cooler is caused to flow into the cold storage temperature zone storage chamber from the first air passage.

9. A refrigerator is characterized in that a refrigerator body is provided with a refrigerator door,

the disclosed device is provided with: a freezing temperature zone storage chamber; a refrigerated temperature zone storage compartment; a cooler for cooling the freezing temperature zone storage chamber; a first air passage for circulating air in the storage chamber; and a second air passage for circulating the air heat-exchanged with the cooler,

the first air passage and the second air passage are adjacent to each other with a partition wall therebetween, and a communication portion for communicating the first air passage and the second air passage is formed,

the communicating portion includes a cold air cutoff unit that cuts off an air flow flowing from the second duct to the first duct.

10. The refrigerator according to claim 9,

the cold air cutting unit is arranged above the uppermost shelf of the cold storage temperature zone storage room.

11. The refrigerator according to claim 2 or 9,

the cross-sectional area of the second air passage is smaller than the cross-sectional areas in the horizontal direction and the vertical direction of a freezing temperature zone storage chamber as a low-temperature chamber.

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