JP7369520B2 - refrigerator - Google Patents

Description

The present invention relates to a household refrigerator-freezer.

Background art in this technical field includes, for example, Japanese Patent Application Laid-Open No. 2007-309634 (Patent Document 1).

In Patent Document 1, the outer shell, which is the main body, is composed of a heat insulating box, and the internal space of the heat insulating box (i.e., the inside of the refrigerator) is divided into a left and right refrigerator compartment and a freezer compartment. A refrigerator is disclosed in which each of the freezer compartments is provided with an evaporator and a centrifugal fan (see, for example, FIG. 1 of Patent Document 1).

Japanese Patent Application Publication No. 2007-309634

The refrigerator described in Patent Document 1 has a cooling system configuration in which the refrigerating compartment and the freezing compartment are provided with centrifugal fans and evaporators that are different in size and have substantially the same size. In addition, in a refrigerator, the amount of cooling required when food at room temperature is placed in the refrigerator compartment is the sensible heat of the food, but the amount of cooling required when food at room temperature is placed in the freezer compartment is the sensible heat and latent heat of the food. There will be more. For this reason, in conventional cooling systems, a problem has been that simply adjusting the rotation speed (air volume) of the centrifugal fan may result in insufficient cooling capacity of the freezer compartment.

comprising a refrigerated storage compartment in a refrigerated temperature range and a frozen storage compartment in a frozen temperature range, a refrigerated evaporator for cooling the refrigerated storage compartment, and blowing air heat exchanged with the refrigerated evaporator to the refrigerated storage compartment. a refrigerating centrifugal fan; a refrigerating evaporator chamber in which the refrigerating evaporator and the refrigerating centrifugal fan are housed; a refrigerating evaporator that cools the freezing storage compartment; A refrigeration centrifugal fan that blows heat-exchanged air to the refrigeration storage chamber, and a refrigeration evaporator chamber in which the refrigeration evaporator and the refrigeration centrifugal fan are housed, the refrigeration centrifugal fan has a discharge area larger than the discharge area of the refrigerating centrifugal fan, and the refrigerating centrifugal fan is a backward-facing fan with a suction port facing the front side. A front end portion of the refrigerating centrifugal fan is disposed on the back side of the refrigerating evaporator than the front end thereof, and the refrigerating centrifugal fan is provided substantially vertically within the refrigerating evaporator chamber. It is characterized in that the suction port is directed toward the back side of the refrigeration evaporator chamber . Other solutions will be described later in the detailed description.

According to the present invention, it is possible to provide a refrigerator that improves the cooling capacity of the freezer compartment without reducing the food storage volume as much as possible.

Front view of a refrigerator according to an example AA sectional view in Figure 1 (a) is a front view of Figure 1 with the door, container, and discharge port removed; (b) is a front view of Figure 1 with the door and container removed. Schematic diagram of the air passage structure showing the flow of cold air in the ice making compartment, freezing compartment, first switching compartment, and second switching compartment according to the example Configuration diagram of a refrigeration cycle of a refrigerator according to an example (a) is a configuration diagram of a refrigeration evaporator according to an example, and (b) is a configuration diagram of a freezing evaporator according to an example. (a) is a perspective view of a refrigeration fan blade according to an example, and (b) is a perspective view of a refrigeration fan blade according to an example. A side cross-sectional view when a turbo fan is vertically mounted in a refrigerator compartment according to an example. Enlarged view of the vicinity of the refrigeration fan in Figure 2 Diagram when the blade diameter of the refrigeration fan in Figure 9(a) is expanded A diagram in which the form of the refrigeration fan in Fig. 9(a) is changed to a propeller fan. An enlarged view of the blade diameter of the propeller fan in Figure 10(a) Enlarged view of the area other than the refrigerator compartment in Figure 3(a) A diagram showing the open/closed state of the damper when the first switching chamber in FIG. 11 is set to freezing mode and the second switching chamber is set to refrigeration mode. Relationship diagram between resistance curve and individual fan characteristics according to the example A perspective view of a refrigeration fan according to an embodiment Detailed view of the central cross section of the refrigeration fan according to the example A diagram showing an example of a driving pattern according to an embodiment

The following are embodiments of the present invention.

An example of a refrigerator related to the present invention will be described. FIG. 1 is a front view of a refrigerator according to an embodiment, and FIG. 2 is a sectional view taken along line AA in FIG.

As shown in FIG. 1, the box body 10 of the refrigerator 1 consists of a refrigerator compartment 2, an ice-making compartment 3 and a freezing compartment 4 installed on the left and right sides, a first switching compartment 5, and a second switching compartment 6, in that order from above. have.

The refrigerator 1 includes doors that open and close the openings of each storage compartment. These doors are divided into left and right rotary refrigerator doors 2a and 2b that open and close the opening of the refrigerator compartment 2, an ice making compartment 3, a freezer compartment 4, a first switching compartment 5, and a second switching compartment 6. These are a pull-out ice making compartment door 3a, a freezer compartment door 4a, a first switching compartment door 5a, and a second switching compartment door 6a, each of which opens and closes. The interior material of these multiple doors is primarily composed of urethane.

The height H1 of the refrigerator compartment 2 is larger than the height H2 of the freezer compartment 4 and the first switching compartment 5 (H1>H2).

Furthermore, when the distance from the floor to the lower ends of the doors 2a and 2b of the refrigerator compartment 2 is H3, and the product height is H4, H3 is 800 to 1200 mm, H4 is 1700 to 2100 mm, and H3 = 950 mm, respectively. , H4=1820 mm. This improves usability because the user can use the refrigerator compartment 2 while standing.

The door 2a is provided with an operation section 200 for controlling the temperature inside the refrigerator. In order to fix the doors 2a and 2b to the refrigerator 1, door hinges (not shown) are provided at the upper and lower parts of the refrigerator compartment 2, and the upper door hinge is covered with a door hinge cover 16.

The refrigerator compartment 2 is a refrigerated storage room whose interior is kept within the refrigerating temperature range (above 0°C), for example, approximately 4°C on average, and the ice making compartment 3 and the freezer compartment 4 are kept within the freezing temperature range (below 0°C ), for example, a frozen storage room kept at an average temperature of about -18°C. The first switching room 5 and the second switching room 6 are switchable storage rooms that can be set to a freezing temperature range or a refrigerating temperature range, for example, a refrigeration mode where the temperature is set to about 4°C on average, and a refrigeration mode where the temperature is set to about -20°C on average. You can switch between freezing mode and freezing mode. In addition, the refrigerator 1 of this embodiment further has a strong refrigerating mode and a weak freezing mode, which have a temperature between the refrigerating mode and the freezing mode, a weak refrigerating mode, which has a higher temperature than the refrigerating mode, and a strong refrigerating mode, which has a temperature lower than the freezing mode. A plurality of operation modes such as a freezing mode are provided, and these operation modes can be selected by operating the operation unit 200.

As shown in FIG. 2, the refrigerator 1 has a box body 10 formed by filling an outer box 10a made of steel plate and an inner box 10b made of synthetic resin with a foamed heat insulating material (for example, urethane foam). The outside and inside of the warehouse are separated. In addition to the foam insulation material, the box body 10 is equipped with a vacuum insulation material with relatively low thermal conductivity between the outer box 10a and the inner box 10b, thereby improving insulation performance without reducing the food storage volume. It's increasing. Here, the vacuum insulation material is constructed by wrapping a core material such as glass wool or urethane with an outer wrapping material. The outer packaging material includes a metal layer (for example, aluminum) to ensure gas barrier properties. Further, each surface of the vacuum heat insulating material is generally formed to have a flat surface shape for ease of manufacture.

In this embodiment, the insulation performance of the refrigerator 1 is improved by providing vacuum insulation materials 25f and 25g on the back and lower part of the box body 10, and vacuum insulation materials 25h (not shown) on both sides of the box body 10. There is.

Similarly, in this embodiment, the insulation performance of the refrigerator 1 is improved by providing vacuum insulation materials 25d and 25e on the first switching room door 5a and the second switching room door 6a. The above-mentioned heat insulation configuration can greatly improve energy saving performance, especially when each of the switching chambers 5 and 6 is in the freezing mode, there is a large temperature difference between the outside of the refrigerator and the switching chambers 5 and 6, and a large amount of heat enters from the outside air.

The refrigerator compartment 2, the ice making compartment 3, and the freezing compartment 4 are separated by a heat insulating partition wall 28. Further, the ice making compartment 3 and the freezing compartment 4 are separated from the first switching compartment 5 by a heat insulating partition wall 29, and the first switching compartment 5 and the second switching compartment 6 are separated by a heat insulating partition wall 30. In the refrigerator 1 of this embodiment, by providing the vacuum heat insulating material 25b inside the heat insulating partition wall 29 and the vacuum heat insulating material 25c inside the heat insulating partition wall 30, heat transfer between storage compartments is suppressed and the heat insulation performance of the refrigerator 1 is improved. is increasing.

Furthermore, in the refrigerator 1 of this embodiment, the F evaporator 14b and its surrounding air passages (the F evaporator chamber 8b, the freezer air passage 12, and the freezer return air passage 12d), which will be described later, and the first switching chamber 5, A heat insulating partition wall 27 is provided between them, and a vacuum heat insulating material 25a is also provided on this heat insulating partition wall 27 to improve the heat insulation performance of the refrigerator 1. The above-mentioned heat insulation configuration can improve the energy saving performance of the refrigerator 1, especially when the first switching compartment 5 is set to the refrigeration mode and the second switching compartment 6 is set to the freezing mode. The first change room 5 in the refrigerating temperature zone absorbs heat from the top (insulating partition wall 29), back (insulating partition wall 27), and bottom (insulating partition wall 30) where the adjacent room is in the freezing temperature zone. Since the switching chamber 5 is excessively cooled, heating with a heater (not shown) may be necessary to maintain the refrigerated temperature range. In the refrigerator of this embodiment, vacuum heat insulating materials 25a, 25b, and 25c are provided inside the heat insulating partition walls 27, 29, and 30, and excessive heat absorption from the top, back, and bottom of the first switching chamber 5 can be suppressed. This makes it easier to maintain the first switching chamber 5 in the refrigerated temperature range, suppresses heating by the heater, and improves energy saving performance.

By providing a plurality of door pockets 33a, 33b, 33c on the inside of the refrigerator compartment doors 2a, 2b, and providing shelves 34a, 34b, 34c, 34d, the inside of the refrigerator compartment 2 is divided into a plurality of storage spaces. There is. The ice-making compartment door 3a, the freezer compartment door 4a, the first switching compartment door 5a, and the second switching compartment door 6a include an ice-making compartment container 3b, a freezer compartment container 4b, a first switching compartment container 5b, and a second switching compartment that are pulled out as one unit. It is equipped with a chamber container 6b.

A refrigerator compartment temperature sensor 41, a freezer compartment temperature sensor 42, a first switching compartment temperature sensor 43, and a second switching compartment temperature sensor 41, a freezer compartment temperature sensor 42, a second switching compartment temperature sensor 43, and a second switching compartment temperature sensor 41 are installed on the back side of the refrigerator compartment 2, the freezing compartment 4, the first switching compartment 5, and the second switching compartment 6, respectively. A switching room temperature sensor 44 is provided, an R evaporator temperature sensor 40a is provided above the R evaporator 14a, and an F evaporator temperature sensor 40b is provided above the F evaporator 14b. The temperatures of the chamber 4, the first switching chamber 5, the second switching chamber 6, the R evaporator 14a, and the F evaporator 14b are detected. Furthermore, an outside air temperature sensor 37 and an outside air humidity sensor 38 are provided inside the door hinge cover 16 on the ceiling of the refrigerator 1 to detect the temperature and humidity of outside air (air outside the refrigerator). In addition, door sensors (not shown) are provided to detect the open and closed states of the doors 2a, 2b, 3a, 4a, 5a, and 6a, respectively.

A control board 31 is disposed on the top of the refrigerator 1, which is equipped with a CPU, memory such as ROM and RAM, an interface circuit, etc., which are part of the control device. The control board 31 also includes an outside air temperature sensor 37, an outside air humidity sensor 38, a refrigerator room temperature sensor 41, a freezer room temperature sensor 42, a first switching room temperature sensor 43, a second switching room temperature sensor 44, and an R evaporator temperature sensor. 40a, F evaporator temperature sensor 40b, etc., are connected by electrical wiring (not shown).

The control board 31 controls the compressor 24, the R fan 9a, the F fan 9b, the dampers 101a, 101b, 102a, 102b, controls the refrigerant control valve 52.

FIG. 3(a) is a front view of the device shown in FIG. 1 with the door, container, and discharge port, which will be described later, removed. The air path and the flow of cold air inside the refrigerator compartment 2 will be explained using FIG. 2 and FIG. 3(a).

As shown in FIGS. 2 and 3(a), the R evaporator 14a, which is a refrigerating evaporator, is provided inside the R evaporator chamber 8a at the back of the refrigerator compartment 2. The air (cold air) that has become low temperature through heat exchange with the R evaporator 14a is passed through the refrigerator compartment air path 11 and the refrigerator compartment discharge port 11a by the R fan 9a, which is a refrigeration fan provided above the R evaporator 14a. Air is blown into the refrigerator compartment 2 through the air, and the inside of the refrigerator compartment 2 is cooled. Here, the form of the R fan 9a is a turbo fan which is a centrifugal fan. The air blown into the refrigerator compartment 2 returns to the R evaporator chamber 8a through the refrigerator compartment return port 15a (see FIG. 2) and the refrigerator compartment return port 15b (see FIG. 3(a)), and is cooled again by the R evaporator 14a. be done.

The refrigerator compartment discharge port 11a of the refrigerator compartment 2 is provided in the upper part of the refrigerator compartment 2, and in this embodiment, it is provided so that air is discharged above the uppermost shelf 34a and the second shelf 34b. Furthermore, the refrigerator compartment return ports 15a and 15b are provided at the lower part of the refrigerator compartment 2, and in this embodiment, the refrigerator compartment return port 15b is located at the second stage from the bottom of the refrigerator compartment 2 (between the shelves 34c and 34d). The refrigerating chamber return port 15a is provided at the lowest stage of the refrigerating chamber 2 (between the shelf 34d and the heat insulating partition wall 28), and approximately at the back of a second indirect cooling chamber 36, which will be described later.

FIG. 3(b) is a front view of FIG. 1 with the door and container removed. Moreover, FIG. 4 is a perspective view of the case 35a that constitutes the first indirect cooling chamber 35 according to the first embodiment. The structure of the first indirect cooling chamber 35 and the flow of cold air around it will be explained using FIG. 3(b) and FIG. 4, and the structure of the second indirect cooling chamber 36 and the surroundings thereof will be explained using FIG. Explain the flow of cold air.

As shown in FIG. 3(b), a first indirect cooling chamber 35 is provided above the shelf 34d in the refrigerator compartment 2. The first indirect cooling chamber 35 includes a case 35a, and has a configuration in which the first indirect cooling chamber 35 is not provided with an outlet for directly blowing cold air.

As shown in FIG. 2, a second indirect cooling chamber 36 is provided inside the refrigerator compartment 2, above the heat insulating partition wall 28. The second indirect cooling chamber 36 has a structure in which the door 36a and the storage section 36b are in contact with each other to be sealed. This prevents low-temperature, low-humidity air from directly entering the food in the second indirect cooling chamber 36, thereby suppressing drying of the food in the second indirect cooling chamber 36. Furthermore, the second indirect cooling chamber 36 of the refrigerator 1 of this embodiment has a structure in which when the door 36a is closed, the door 36a and the storage section 36b are brought into contact with each other without a gap, for example, by packing, and are sealed. In addition, a pump (not shown) is connected to the second indirect cooling chamber 36, and by operating the pump, the pressure inside the second indirect cooling chamber 36 is reduced to, for example, 0.8 atm. Oxidation of the food provided in the double indirect cooling chamber 36 is suppressed.

The second indirect cooling compartment 36 is adjacent to the ice making compartment 3 and the freezing compartment 4 via the heat insulating partition wall 28, and is in an ice temperature mode (lower temperature than the refrigerator compartment 2) due to heat absorption by the ice making compartment 3 and the freezing compartment 4. For example, it can be heated to temperatures between approximately -3°C and 0°C. Further, a heater (not shown) is provided in the heat insulating partition wall 28, and by operating the heater, a chilled mode (for example, about 0 to 3° C.), which is close to the temperature of the refrigerator compartment 2, can be set. Note that these operation modes can be switched by operating the operation unit 200.

FIG. 4 is a schematic diagram of an air passage structure showing the flow of cold air in the ice making compartment 3, the freezing compartment 4, the first switching compartment 5, and the second switching compartment 6 according to the first embodiment. The air passage configuration inside the refrigerator compartment other than the refrigerator compartment 2 and the flow of cold air will be explained using FIGS. 2 and 4.

As shown in FIGS. 2 and 4, the F evaporator 14b, which is a freezing evaporator, is provided in the F evaporator chamber 8b at the back of the first switching chamber 5 and the second switching chamber 6. The air (cold air) that has become low temperature by exchanging heat with the F evaporator 14b is transferred to the freezer compartment air passage 12, the freezer compartment outlet 12a, Air is blown to the ice making compartment 3 and the freezing compartment 4 through the ice making compartment 3, cooling the water in the ice tray 3c of the ice making compartment 3, the ice in the container 3b, the food in the container 4b of the freezing compartment 4, etc. Here, the form of the R fan 9a is a turbo fan which is a centrifugal fan. The air that has cooled the ice making compartment 3 and the freezing compartment 4 returns to the F evaporator compartment 8b from the freezing compartment return port 12c via the freezing compartment return air path 12d, and is cooled again by the F evaporator 14b.

In the refrigerator 1 of this embodiment, the first switching chamber 5 and the second switching chamber 6 are also cooled with air (cold air) made low in temperature by the F evaporator 14b. The blowing of cold air to the first switching chamber 5 and the second switching chamber 6 is controlled by dampers 101a, 101b, 102a, and 102b, which are blowing control sections.

First, the flow of cold air to the first switching chamber 5 will be explained. The flow of cold air in the first switching chamber 5 differs between freezing mode and refrigeration mode. When the first switching chamber 5 is in the freezing mode, the damper 101a is opened and the damper 101b is closed. The air cooled by the F evaporator 14b passes through the F fan 9b, the freezer air passage 12, the damper 101a, and the first switching chamber outlet 111a, which is a direct cooling outlet of the first switching chamber 5, to the first switching chamber 5. Air is blown into the first changing room container 5b provided in the first changing room 5, and the food in the first changing room container 5b is cooled. Since the cold air directly cools the food in the first changing chamber container 5b, the food in the first changing chamber container 5b can be cooled in a relatively short time.

When the first switching chamber 5 is in the refrigerating mode, the damper 101a is closed and the damper 101b is opened. The air cooled by the F evaporator 14b passes through the F fan 9b, the freezer air passage 12, the damper 101b, and the first switching chamber outlet 111b, which is an indirect cooling outlet of the first switching chamber 5, to the first switching chamber 5. All air is blown to the outside (outer periphery) of the changeable chamber container 5b. It becomes difficult for the cold air to directly reach the food in the first changing chamber container 5b, that is, the food is indirectly cooled through the first changing chamber container 5b, so that the food can be cooled while suppressing drying. The air discharged from the first switching chamber discharge port 111a or the first switching chamber discharge port 111b and cooling the inside of the first switching chamber 5 is passed from the first switching chamber return port 111c through the freezing chamber return air path 12d to the F It returns to the evaporator chamber 8b and is cooled again by the F evaporator 14b.

Next, the flow of cold air to the second switching chamber 6 will be explained. The configuration of the second switching chamber 6 is similar to that of the first switching chamber 5, and the opening and closing of the damper is changed depending on the operation mode. When the second switching chamber 6 is in the freezing mode, the damper 102a is opened and the damper 102b is closed. The air (cold air) cooled by the F evaporator 14b is passed through the F fan 9b, the freezer air passage 12, the damper 102a, and the second switching chamber outlet 112a, which is a direct cooling outlet of the second switching chamber 6. Then, air is blown into the second switching chamber container 6b to cool the food on the second switching chamber container 6b. Since the cold air directly cools the food in the second switching chamber container 5b, the food in the second switching chamber container 6b can be cooled in a relatively short time.

When the second switching chamber 6 is in the refrigerating mode, the damper 102b is opened and the damper 102a is closed. The air cooled by the F evaporator 14b passes through the F fan 9b, the freezer air passage 12, the damper 102b, and the second switching chamber outlet 111b, which is an indirect cooling outlet for the second switching chamber 6, to the second switching chamber 6. Air is blown to the outside (outer periphery) of the two-switchable chamber container 6b to indirectly cool the food while suppressing drying of the food. The air that has cooled the second switching chamber 6 returns to the F evaporator chamber 8b from the second switching chamber return port 112c via the freezing chamber return air path 12d, and is cooled again by the F evaporator 14b.

FIG. 5 is a configuration diagram of the refrigeration cycle of the refrigerator according to the first embodiment. In the refrigerator 1 of this embodiment, the compressor 24, the external radiator 50a which is a heat radiating means for radiating heat from the refrigerant, the wall heat radiation pipe 50b, and the dew condensation prevention that suppresses dew condensation on the front parts of the partition walls 28, 29, and 30. Piping 50c, a refrigerating capillary tube 53a and a freezing capillary tube 53b, which are depressurizing means for reducing the pressure of the refrigerant, and an R evaporator 14a and an F evaporator that exchange heat between the refrigerant and the air inside the refrigerator to absorb heat inside the refrigerator. 14b, and these cool the inside of the refrigerator. It also includes a dryer 51 that removes moisture in the refrigeration cycle, gas-liquid separators 54a and 54b that prevent liquid refrigerant from flowing into the compressor 24, and a three-way valve 52 that controls the refrigerant flow path, and a check valve. It also includes a valve 56 and a refrigerant merging section 55 that connects the refrigerant flow, and these are connected by a refrigerant pipe 59 to constitute a refrigeration cycle.

Note that the refrigerator 1 of this embodiment uses isobutane as a refrigerant. Furthermore, the compressor 24 of this embodiment is equipped with an inverter so that the rotation speed can be changed.

The three-way valve 52 is a member that is provided with two outlet ports 52a and 52b, and has a refrigeration mode in which the refrigerant flows through the outlet port 52a side and a freezing mode in which the refrigerant flows in the outlet port 52b side, and is capable of switching between these modes. Furthermore, the three-way valve 52 of this embodiment has a fully closed mode in which refrigerant does not flow through either the outlet 52a or the outlet 52b, and a fully open mode in which the refrigerant flows in both, and can be switched to either of these modes. It is possible.

In the refrigerator 1 of this embodiment, the refrigerant flows as follows. The refrigerant discharged from the compressor 24 flows in this order through the external radiator 50a, the external radiator 50b, the condensation prevention piping 50c, and the dryer 51, and reaches the three-way valve 52. An outlet 52a of the three-way valve 52 is connected to a refrigerating capillary tube 53a via a refrigerant pipe, and an outlet 52b is connected to a freezing capillary tube 53b via a refrigerant pipe.

When cooling the refrigerator compartment 2, the refrigerant is made to flow toward the outlet 52a. The refrigerant flowing out from the outlet 52a flows through the refrigerating capillary tube 53a, the R evaporator 14a, the gas-liquid separator 54a, and the refrigerant confluence section 55 in this order, and then returns to the compressor 24. The refrigerant that has become low pressure and low temperature in the refrigeration capillary tube 53a flows through the R evaporator 14a, and the R evaporator 14a becomes low temperature.The air cooled by the R evaporator 14b is blown by the R fan 9a (see FIG. 2). By doing so, the refrigerator compartment 2 is cooled.

When cooling the ice making compartment 3, the freezing compartment 4, the first switching compartment 5, and the second switching compartment 6, the refrigerant is made to flow toward the outlet 52b. The refrigerant flowing out from the outlet 52b flows through the freezing capillary tube 53b, the F evaporator 14b, the gas-liquid separator 54b, the check valve 56, and the refrigerant merging section 55 in this order, and then returns to the compressor 24. The check valve 56 is arranged so that the refrigerant flows from the gas-liquid separator 54b to the refrigerant confluence section 55, but does not flow from the refrigerant confluence section 55 to the gas-liquid separator 54b. The refrigerant, which has become low pressure and low temperature in the freezing capillary tube 53b, flows through the F evaporator 14b, so that the F evaporator 14b becomes low temperature, and the air cooled by the F evaporator 14b is blown by the F fan 9b (see FIG. 2). This cools the ice making compartment 3, the freezing compartment 4, the first switching compartment 5, and the second switching compartment 6.

In the refrigerator 1 of this embodiment, the refrigerator compartment 2 is cooled using the R evaporator 14a, and the ice making compartment 3, the freezing compartment 4, the first switching compartment 5, and the second switching compartment 6 are cooled using the F evaporator 14b. However, with such a configuration, different evaporator temperatures can be set for each of the R evaporator 14a and the F evaporator 14b. Specifically, when the refrigerant is passed through the F evaporator 14b that cools the ice making compartment 3, the freezing compartment 4, the first switching compartment 5, and the second switching compartment 6, which are in the freezing temperature range or can be set to the freezing temperature range. The temperature of the evaporator is lower than that of these storage chambers (for example, −25° C.). On the other hand, when the refrigerant is passed through the R evaporator 14a that cools the refrigerator compartment 2 in the refrigeration temperature range, the evaporator temperature of the refrigerant is set relatively high (for example, -10° C.). Generally, the higher the temperature of the evaporator, the higher the cooling efficiency of the refrigeration cycle, which is effective in improving energy saving performance. Furthermore, the higher the temperature of the evaporator, the more frost formation of moisture in the air when the air passes through the evaporator is suppressed, that is, the dehumidification of the air is suppressed, and the inside of the refrigerator can be kept at high humidity. Therefore, by cooling the refrigerator compartment 2 while the temperature of the R evaporator 14a is high, the energy saving performance when cooling the refrigerator compartment 2 can be improved compared to the case where the refrigerator compartment 2 is cooled by a common evaporator with a storage compartment in the freezing temperature range. At the same time, the inside of the refrigerator compartment 2 can be kept at high humidity.

In addition, by separating the R evaporator 14a that cools only the refrigerator compartment 2 and the F evaporator 14b that cools other storage compartments, the defrosting method of the R evaporator 14a is set to off-cycle defrosting, resulting in further energy-saving performance. The aim is to increase the humidity of the refrigerator compartment 2.

First, a radiant heater 21 for heating the F evaporator 14b is provided below the F evaporator 14b. The radiant heater 21 is, for example, an electric heater of 50W to 200W, and is 150W in this embodiment. Defrosting water (melted water) generated during defrosting of the F evaporator 14b is sent from the F toy 23b at the bottom of the F evaporator chamber 8b to the F evaporation tray 32 provided at the top of the compressor 24 via the F drain pipe 26. be discharged.

On the other hand, an off-cycle defrosting method is adopted for defrosting the R evaporator 14a, and the R fan 9a is driven without flowing refrigerant to the R evaporator 14a. The air in the refrigerator compartment 2 flows through the refrigerator compartment return ports 15a and 15b to the R evaporator 14a by the R fan 9a (see FIGS. 2 and 3(a)), and the refrigerator temperature (0 The frost in the R evaporator 14a is heated and defrosted by the air in the refrigerator compartment 2 (at a temperature of 15°C or higher). Defrosting water generated during defrosting of the R evaporator 14a is supplied to the machine room 39 from the R toy 23a (see FIG. 2) provided at the bottom of the R evaporator chamber 8a via an R drain pipe (not shown). The liquid is discharged to an R evaporating dish (not shown).

When using the off-cycle defrosting method, the R evaporator 14a can be defrosted using only a fan (0.5 to 3 W) without using an electric heater (approximately 150 W), so it consumes less power than a defrosting method that uses an electric heater. You can save electricity. In addition, the air (approximately 4°C) passing through during off-cycle defrosting is cooled by the low temperature R evaporator 14a and the frost (approximately 0°C) adhering to the R evaporator 14a. The refrigerator compartment 2 can be cooled at the same time as frosting. Therefore, it is a defrosting method with high energy-saving performance. Furthermore, since the temperature of the R evaporator 14a is high during off-cycle defrosting, dehumidification of the air passing through the R evaporator 14a is suppressed or humidified, which further enhances the effect of keeping the refrigerator compartment 2 at high humidity. be able to.

In this way, by providing the R evaporator 14a that cools the refrigerator compartment 2, which is a storage compartment in the refrigeration temperature range, and increasing the evaporator temperature when cooling the refrigerator compartment 2, and by adopting an off-cycle defrosting method, It improves energy saving performance and also makes the refrigerator compartment 2 highly humid.

FIG. 6 is a block diagram of the evaporator of the refrigerator according to the embodiment, FIG. 6(a) is a block diagram of the refrigeration evaporator, and FIG. 6(b) is a block diagram of the freezing evaporator. As shown in FIG. 6, the R evaporator 14a and the F evaporator 14b are cross-fin tube heat exchangers, in which a plurality of aluminum fins 57 are connected to an aluminum heat transfer tube 58 that is bent a plurality of times. It is structured so that it penetrates.

In this embodiment, the relationship between the average fin stack spacing Pf1 of the R evaporator 14a and the average fin stack spacing Pf2 of the F evaporator 14b is configured to be Pf1≦Pf2, and further, the height H5 of the R evaporator 14a and By configuring the height H6 of the F evaporator 14b to satisfy H5≦H6, it is possible to both expand the food storage volume and suppress a decrease in cooling performance.

In the R evaporator 14a, since an off-cycle defrosting method is used for the defrosting method, power consumption is unlikely to increase when Pf1 is narrowed and frost clogging becomes more likely to occur. Therefore, the R evaporator 14a is compactly mounted with a relatively small height H1 and a relatively narrow Pf1, thereby expanding the food storage capacity of the refrigerator compartment 2 without reducing cooling performance as much as possible.

In the F evaporator 14b, since a heater defrosting method is used for the defrosting method, the cooling performance tends to deteriorate when Pf2 is relatively narrowed and frost clogging is likely to occur. Therefore, by widening Pf2, the number of times the cooling performance deteriorates is reduced.

In this example, Pf1 is approximately 3 mm, Pf2 is approximately 5 mm, H5 is approximately 90 mm, and H6 is approximately 150 mm, but the relationships Pf1≦Pf2 and H5≦H6 hold true even in the case of dimensions other than those used in this example. A similar effect can be obtained.

FIG. 7(a) is a perspective view of a refrigeration fan blade according to an embodiment. As shown in FIG. 7(a), the configuration of the R fan 9a is a turbo fan (backward-facing fan) which is a centrifugal fan, and has a blade diameter D1 = 100 mm, a blade height L1 = 25 mm, and the number of blades is 10. . Further, the rotation speed is approximately 1000 to 1800 rpm.

FIG. 8 is a side sectional view of the case where a turbo fan is vertically mounted in the refrigerator compartment according to the embodiment. In the refrigerator of this embodiment, a turbo fan, which is a centrifugal fan, is arranged substantially vertically as the R fan 9a. Further, the front end of the R fan 9a is located closer to the back side than the front end of the R evaporator 14a. The vertical projection of the R fan 9a and the vertical projection of the evaporator 14a at least partially overlap, and in this embodiment, the vertical projection of the R fan 9a is located within the vertical projection of the evaporator 14a. ing.

Centrifugal fans such as turbo fans have the characteristic of blowing out the flow sucked in in the axial direction in the radial direction, so in this embodiment, a space is required on the R fan 9a suction port side (front side of the refrigerator). However, there is no need to provide an air passage space on the back side of the R fan 9a. Therefore, the depth dimension 60 of the air passage around the R fan 9a can be made equal to or less than the depth dimension 61 of the R evaporator 14a, which can contribute to expanding the food storage volume. "Equivalent" here means that the depth dimension 60 of the air passage around the R fan 9a is within ±20%, preferably within ±10%, with respect to the depth dimension 61 of the R evaporator 14a. In addition, when the partition 62 is not straight in the vertical direction, the depth dimension 60 of the air passage is an average in the height range from the upper end to the lower end of the R fan 9a.

Additionally, since turbo fans are high static pressure type blowers, they have the ability to easily increase air volume when static pressure is high (air resistance is high) compared to propeller fans commonly used in refrigerators. In this embodiment, Pf1 of the R evaporator 14a is narrower than Pf2 of the F evaporator 14b, and off-cycle defrosting is adopted, so the frequency at which frost grows in the R evaporator 14a and increases air path resistance However, even under such operating conditions, cooling can be performed using the latent heat of frost without significantly reducing the air volume.

FIG. 7(b) is a perspective view of the refrigeration fan blade according to the embodiment. As shown in FIG. 7(b), the form of the F fan 9b is a turbo fan (rearward-facing fan) that is a centrifugal fan, with blade diameter D2 = 120 mm, blade height L2 = 26 mm, and the number of blades is 10. . Further, the rotation speed is approximately 1000 to 1800 rpm.

As shown in FIGS. 8(a) and 8(b), the discharge area of the F fan 9b (A2=D2×π×L2) is made larger than the discharge area of the R fan 9a (A1=D1×π×L1). It consists of Here, the discharge area refers to the area defined by the blade height and blade diameter, and does not include parts other than the blades. Considering the case where the same food (cooling load) is put into the refrigerator compartment 2 in the refrigeration temperature range and the freezer compartment 3 in the freezing temperature range, the amount of cooling required in the freezer compartment 3 will be greater than that in the refrigerator compartment 2. For example, by setting the rotation speed of the R fan 9a and the F fan 9b to be about the same and making the relationship A1 < A2, the amount of air blown to the refrigerator compartment 2 will be less than the amount of air blown to the freezer compartment 3. It becomes easier to blow the amount of cold air suitable for the required amount of cooling. The above effect becomes more effective when the first switching chamber 5 is in the freezing mode and when the second switching chamber 6 is in the freezing mode.

In this embodiment, it is assumed that the rotation speeds of the two fans are about the same, but for example, if the required cooling amount on the refrigeration side becomes larger than expected, the rotation speed of the refrigeration side fan may be increased. If the required cooling amount on the refrigeration side is larger than expected, the same effect can be obtained by increasing the rotation speed of the refrigeration side fan.

As shown in FIGS. 2, 7(a) and 7(b), the discharge area A2 of the fan that is farther from the user's face level is greater than the fan discharge area A1 located in the storage room that is closer to the user's face level. is increasing. As a result, even if noise increases due to an increase in the discharge area A2, since the distance between the user and the F fan 9b is relatively long, the user is less likely to notice the increase in noise, improving comfort. .

As shown in FIG. 7(b), the F fan 9a is a turbo fan that is a centrifugal fan. Turbofans can be designed with a relatively smaller number of blades than other centrifugal fans (eg, sirocco fans, radial fans). This means that the effective area that can be used as an air path is large, so even if frost grows near the narrow suction opening, the air volume is less likely to drop drastically.In other words, the cooling capacity will decrease. This makes it less likely that this will occur, so the air volume (cooling capacity) can be improved when the refrigerator is operated for a long time.

As shown in FIGS. 7(a) and 7(b), the R fan 9a and the F fan 9b are turbofans, and the blade height L1 of the R fan 9a and the blade height L2 of the F fan 9b are approximately the same, and The configuration is such that the blade diameter D2 of the F fan 9b is larger than the blade diameter D1 of the fan 9a, in other words, the relationship D2/D1>L2/L1 holds true. By establishing the above relationship, the depth 63 of the F evaporator chamber (see FIG. 10 described later) does not need to be expanded in accordance with the expansion of the discharge area A2 of the F fan 9b, so that the food storage capacity can be expanded. It is possible to improve the cooling performance on the freezing side. The above effects will be explained in detail using FIGS. 9 and 10.

9(a) is an enlarged view of the vicinity of the refrigeration fan in FIG. 2, and FIG. 9(b) is an enlarged view of the blade diameter of the refrigeration fan in FIG. 9(a). Moreover, FIG. 10(a) is a diagram in which the form of the refrigeration fan in FIG. 9 is a propeller fan, and FIG. 10(b) is a diagram in which the blade diameter of the propeller fan in FIG. 10(a) is enlarged.

As shown in FIGS. 10A and 10B, a propeller fan that is an axial fan is often used as the F fan 9b. When the F fan 9b is a propeller fan, it is installed horizontally or inclined to ensure space for the inflow and outflow of the fan, so if the fan blade diameter D2 is increased, the depth of the F evaporator chamber is 63. Since the food storage space is expanded and implemented, the food storage capacity is reduced.

Therefore, in this embodiment, as shown in FIGS. 9(a) and 9(b), the F fan 9b is configured as a turbo fan, which is a centrifugal fan, so that the F fan 9b can be installed approximately vertically. Even if the fan blade diameter D2 is designed to be large for the purpose of increasing the air volume, it can be implemented without enlarging the depth 63 of the F evaporator chamber.

As shown in FIG. 9A, since the turbo fan generates a vortex near the inlet, the wind speed distribution 64 at the outlet of the F fan 9b has a characteristic that the wind speed is faster on the front side of the refrigerator 1. Therefore, by arranging the inflow port of the F fan 9b on the back side of the refrigerator 1, the flow with high wind speed reaches the discharge ports 111a and 112a in a relatively short distance, reducing air path loss. The cooling capacity of the first switching chamber 5, which has a relatively large internal volume, can be improved.

FIG. 11 is an enlarged view of the parts other than the refrigerator compartment in FIG. 3(a). Moreover, FIG. 11 also shows the open and closed states of the dampers 101a, 101b, 102a, and 102b when the first switching chamber 5 and the second switching chamber 6 are set to the freezing mode. As shown in FIG. 11, air discharged from the F fan 9b flows toward dampers 101a and 102a located in the fan radial direction (left, right, top, and bottom). Therefore, by installing a centrifugal fan that blows out in the fan radial direction in the air path formed in the fan radial direction, the cold air flowing out from the F fan 9b can be carried to the discharge port without being directed greatly. Air path loss can be reduced. Due to the above effects, the amount of air passing through the F fan 9b can be increased.

In this embodiment, the angle formed by the straight line connecting the damper 101a and the center of the fan and the straight line connecting the damper 102a and the center of the fan (the angle formed by the two straight lines connecting the damper in the open state and the center of the fan), The maximum value) is about 120 degrees, and a great effect can be expected when this angle is about 90 degrees or more.

Further, this embodiment has a plurality of dampers such as dampers 101a, 101b, 102a, and 102b, and the operation mode is switched by opening and closing the dampers. In this way, in a refrigerator in which the operation mode is switched by opening and closing a plurality of dampers, the open and closed states of the dampers 101a, 101b, 102a, and 102b are changed before the cold air flowing out from the F fan 9b reaches the discharge ports 111a, 111b, 112a, and 112b. In some cases, the wind path resistance increases dramatically.

FIG. 12 is a diagram showing the open/closed state of the damper when the first switching chamber and the second switching chamber in FIG. 11 are set to the refrigeration mode. As shown in FIG. 12, when the first switching chamber 5 and the second switching chamber 6 are set to the refrigeration mode, the dampers 101a and 102a are opened and the dampers 101b and 102b are closed. Therefore, the maximum value of the angle formed by the two straight lines connecting the damper in the open state and the center of the fan is approximately 30°, so the air passage area is reduced compared to approximately 120° in Figure 12, and the air passage resistance is reduced. As a result, the air volume decreases. Therefore, it is desirable to select a fan configuration that does not easily reduce the air volume even when the air path resistance increases.

FIG. 13 shows a relationship diagram between the resistance curve and the fan unit characteristics according to the first embodiment. FIG. 13 shows fan characteristics when a propeller fan of approximately 110 mm is driven at 1500 rpm as a representative example of a commonly used blower, fan characteristics when a turbo fan of approximately 120 mm used in this embodiment is driven at 1500 rpm, and The first resistance curve when the dampers 101a and 102a are opened and the dampers 101b and 102b are closed (operating mode in FIG. 11), and the second resistance curve when the dampers 101b and 102b are opened and the dampers 101a and 102a are closed. 12 shows a resistance curve (operating mode of FIG. 12). Here, the first resistance curve is when the first switching chamber 5 and the second switching chamber 6 are in the freezing mode, and the air path resistance is relatively small. Moreover, the second resistance curve is a case where the first switching chamber 5 and the second switching chamber 6 are in the freezing mode, and the air path resistance is relatively large. In this way, if a propeller fan is used as the F fan 9b when there is a clear difference in air path resistance, the air volume will decrease by about 30% due to the difference in operation mode. On the other hand, if a turbo fan is used as in this embodiment, the air volume will only decrease by about 20% depending on the operating mode. Furthermore, when the first switching chamber 5 and the second switching chamber 6, which require the most air volume, are in the freezing mode, in other words, the air volume when a propeller fan is installed and the turbo fan at the first resistance curve. When comparing the air volume when installed, the turbo fan has about 10% more air volume.

FIG. 14 is a perspective view of the refrigeration fan according to the embodiment, and FIG. 15 is a central sectional view of FIG. 14. In this embodiment, the F fan 9b includes a blade 70, a brushless motor 71, a fixing part 76 for fixing the fan to the heat insulating partition wall 27, a board 77 provided on the fixing part 76 to control the brushless motor 71, and a board 77 for controlling the brushless motor 71. It is composed of an F fan temperature sensor 78 provided and electrical wiring (not shown) connected to the board 77. Further, the brushless motor 71 is an outer rotor type that includes a motor shaft 72, a bearing 73, a rotor 74, a stator 75, and the like.

As shown in FIG. 15, in this embodiment, in addition to the F evaporator temperature sensor 40b provided at the top of the F evaporator as a first temperature sensor for confirming the completion of defrosting, a second temperature sensor is also provided. An F fan temperature sensor 78 is provided. Further, the F evaporator temperature sensor 40b is mounted closer to the F evaporator 14b than the F fan 9b, and the F fan temperature sensor 78 is mounted closer to the F fan 9b than the F evaporator 14b. By arranging it in this way, it is easy to check whether the frost attached to the F evaporator 14b has melted using the first temperature sensor, and whether the frost attached to the F fan 9b has melted using the second temperature sensor. Since it is easy to check, more reliable defrosting is possible than when the defrosting state is detected using only the first temperature sensor.

As shown in FIG. 15, the F fan 9a is a turbo fan that is a centrifugal fan. Turbofans can be designed with a relatively smaller number of blades than other centrifugal fans (eg, sirocco fans, radial fans). This is because the effective area that can be used as an air path is wide, so even if frost grows near the suction opening, the air volume is unlikely to drop significantly.

Furthermore, if the F fan temperature sensor 78 is mounted in the projection area 79 of the blade in the rotational axis direction, the melting state of the frost attached to the blade 70 and its surroundings can be detected more efficiently.

In addition, as in this embodiment, by bringing a part of the F fan temperature sensor 76 into contact with a part of the parts (blade 70, brushless motor 71, fixed part 76, board 77) that constitute the F fan 9b, , the state of frost adhering to the blades 71 and the surrounding air passages can be easily detected by heat conduction.

As shown in FIG. 15, in addition to the radiant heater 21 (see FIG. 2), which is the first defrosting heater, a plate heater 80 is installed as the second defrosting heater. Further, the radiant heater 21 is mounted closer to the F evaporator 14b than the F fan 9b, and the plate heater 80 is mounted closer to the F fan 9b than the F evaporator 14b. With this arrangement, by driving the radiant heater 21, which is the first defrosting heater, and the plate heater 80, which is the second defrosting heater, the blade 70 can Since it becomes easier to defrost the blades 70 and the surrounding air passages, blockage of the blades 70 and the surrounding air passages becomes less likely to occur, making it possible to defrost with high reliability.

Further, if the plate heater 80 is mounted in the rotation axis direction projection area 79 of the blade as in this embodiment, the frost attached to the blade 70 and its surroundings can be melted more efficiently.

Furthermore, as in this embodiment, by bringing a part of the plate heater 80 into contact with a part of the parts (blade 70, brushless motor 71, fixed part 76, board 77) constituting the F fan 9b, even higher efficiency can be achieved. Frost attached to the blades 70 and surrounding air channels can be melted.

In addition, by providing the plate heater 80 on the back side of the F fan 9b, it becomes easier to heat the blades 70 by heat conduction via the motor shaft 72, making it easier to melt frost on the blades 70 and the surrounding area. Furthermore, in this embodiment, the configuration of the brushless motor 71 is an outer rotor type, which makes it easier to shorten the motor shaft 71 than an inner rotor type.In other words, by shortening the distance from the plate heater 80 to the blades 70, , making it easier to melt.

Further, as shown in FIG. 15, in this embodiment, a vacuum heat insulating material 25a is provided between the plate heater 80 and the storage chamber (switching chamber 5 in this embodiment). Therefore, the heat of the plate heater 80 is efficiently transmitted to the F fan 9b side, making it easier to melt frost attached to the blades 70 and the surrounding air passages.

FIG. 16 is a diagram showing an example of a driving pattern related to the embodiment. Here, a case where the outside air is relatively high temperature (for example, 32° C.) and not low humidity (for example, 60% RH) is shown. In addition, the first switching chamber 5 is set to the refrigeration operation mode, and the second switching chamber 6 is set to the refrigeration operation mode, and the operations of the radiant heater 21, plate heater 80, F fan 9b, and compressor 24 are controlled. Excerpted temperatures of the switching chamber 6, F fan temperature sensor 78, and F evaporator temperature sensor 40b are shown.

In the cooling operation in which the first switching chamber 5 is in the freezing operation mode and the second switching chamber 6 is in the refrigerating operation mode, the compressor 24 is driven to flow refrigerant to the F evaporator 14b, and the F freezing evaporator 14b is heated to a low temperature. Make it. By operating the F fan 9b in this state, the ice making compartment 3, the freezing compartment 4, and the first switching compartment 5 are cooled by blowing the low-temperature air that passes through the F evaporator 14b. At time t ₁ (in the refrigerator of this embodiment, the predetermined time has passed since the end of the previous defrosting and the defrosting is started again), the F fan 9b and the compressor 24 are stopped, and the radiant heater 21 and plate are stopped. Defrosting operation is started by starting the heater 80. Through this defrosting operation, not only the F evaporator 14b but also the frost and ice that have grown on the blades 70 of the F fan 9b and the surrounding air passages can be melted as well. In this defrosting operation, when the temperature of the F fan temperature sensor 78 reaches T _DR (T _DR = 3° C. in the refrigerator of this embodiment), the plate heater 80 is stopped (time t ₂ ), and the F evaporator temperature sensor When the temperature of 40b reaches _TDR , the radiant heater 21 is stopped (time _t3 ), and the defrosting operation is performed until these two heaters are stopped (time _t3 ). Here, the plate heater 80 and the radiant heater 21 are not stopped at the same time, but are stopped separately depending on the sensor temperature near each heater, thereby suppressing excessive heating of the air passage around the heater and improving energy saving performance. are doing.

In addition, in this embodiment, the radiant heater 21 and the plate heater 80 are used for defrosting, and the F evaporator temperature sensor 40b and the F fan temperature sensor 78 are used to control the defrosting end time, thereby eliminating frost and ice. Achieves highly reliable defrosting with little thawed residue.

When the conditions for ending the defrosting operation are satisfied, the compressor 24 is driven to flow the refrigerant into the F evaporator 14b to bring it to a low temperature, and the F fan 9b is started again, so that the ice making compartment 3, the freezing compartment 4, and the The changing room 5 is completely cooled down.

The refrigerator of this embodiment only needs to have the above characteristics when evaluating the average temperature of the components in periodic control, and even if the characteristics differ locally or in the short term, the same characteristics will be maintained. Effects can be obtained.

The above are examples showing this embodiment. Note that the present invention is not limited to the embodiments described above, and includes various modifications. For example, the embodiments described above are described in detail to explain the present invention in an easy-to-understand manner, and the present invention is not necessarily limited to having all the configurations described. Furthermore, it is possible to add, delete, or replace some of the configurations of the embodiments with other configurations.

1 Refrigerator 2 Refrigerator compartment 2a, 2b Refrigerator compartment door 3 Ice making compartment 3a Ice making compartment door 3b Ice making compartment container 3c Ice tray 4 Freezer compartment 4a Freezer compartment door 4b Freezer compartment container 5 First changing room 5a First changing room door 5b First Switching chamber container 6 Second switching chamber 6a Second switching chamber door 6b Second switching chamber container 8a R evaporator room (refrigeration evaporator room)
8b F evaporator room (refrigeration evaporator room)
9a R fan (refrigeration fan)
9b F fan (refrigeration fan)
10 Insulating box body 10a Outer box 10b Inner box 11 Refrigerator room air path 11a Refrigerator room outlet 12 Freezer room air path 12a Ice making room outlet 12b Freezer room outlet 12c Freezer room return port 12d Freezer room return air path 14a R evaporator (refrigeration evaporator)
14b F evaporator (refrigeration evaporator)
15a, b Refrigerator compartment return port 16 Hinge cover 21 Radiant heater 23a R toy 23b F toy 24 Compressor 25a, 25b, 25c, 25d, 25e, 25f, 25g, 25h Vacuum insulation material 26 F drain pipe 27, 28, 29, 30 Heat insulating partition wall 31 Control board 32a R evaporation tray 32b F evaporation tray 34a R shelf top 34b R shelf 2nd tier 34c R shelf 3rd tier 34d R shelf bottom 35 First indirect cooling chamber 36 Second indirect cooling chamber 37 Ice making tank 39 Machine room 40a R evaporator temperature sensor 40b F evaporator temperature sensor 41 Refrigerator room temperature sensor 42 Freezer room temperature sensor 43 First switching room temperature sensor 44 Second switching room temperature sensor 45 Toy temperature sensor 50a, 50b radiator 51 Dryer 52 Three-way valve (refrigerant control means)
53a Refrigeration capillary tube (decompression means)
53b Freezing capillary tube (decompression means)
54a Refrigeration gas-liquid separator 54b Refrigeration gas-liquid separator 55 Refrigerant confluence section 56 Check valve 57 Fin 58 Heat transfer tube 59 Refrigerant piping 60 Depth dimension of air passage around R fan 9a 61 Depth dimension of R evaporator 14a 62 Partition 63 Depth of F evaporator chamber 64 Maximum value of the angle between two straight lines connecting the open damper and the center of the fan 65 Wind speed distribution 70 Blades 71 Brushless motor 72 Motor shaft 73 Bearing 74 Stator 75 Rotor 76 Fixed part 77 Board 78 F fan temperature sensor 79 Air path space 80 on the projection surface of F fan 9b Plate heaters 101a, 101b, 102a, 102b Damper (air blow control section)
111a, 111b First switching chamber discharge port 111c First switching chamber return port 112a, 112b Second switching chamber discharge port 112c Second switching chamber return port 200 Operation section

Claims (5)

comprising a refrigerated storage compartment in a refrigerated temperature range and a frozen storage compartment in a frozen temperature range, a refrigerated evaporator for cooling the refrigerated storage compartment, and blowing air heat exchanged with the refrigerated evaporator to the refrigerated storage compartment. a refrigerating centrifugal fan; a refrigerating evaporator chamber in which the refrigerating evaporator and the refrigerating centrifugal fan are housed; a refrigerating evaporator that cools the freezing storage compartment; A refrigeration centrifugal fan that blows heat-exchanged air to the refrigeration storage chamber, and a refrigeration evaporator chamber in which the refrigeration evaporator and the refrigeration centrifugal fan are housed, the refrigeration centrifugal fan has a discharge area larger than the discharge area of the refrigerating centrifugal fan, and the refrigerating centrifugal fan is a backward-facing fan with a suction port facing the front side. A front end portion of the refrigerating centrifugal fan is disposed on the back side of the refrigerating evaporator than the front end thereof, and the refrigerating centrifugal fan is provided substantially vertically within the refrigerating evaporator chamber. A refrigerator characterized in that a suction port is directed toward the back side of the evaporator chamber for freezing . In the refrigerator according to claim 1, when the centrifugal fan for refrigeration has a blade diameter of D2 and a blade height of L2, and the centrifugal fan for refrigeration has a blade diameter of D1 and a blade height of L1, then D2/D1> A refrigerator characterized in that an L2/L1 relationship holds. 3. The refrigerator according to claim 1, wherein the freezing centrifugal fan is a backward-facing fan. In the refrigerator according to any one of claims 1 to 3 , the relationship between the average fin pitch Pf1 of the refrigeration evaporator and the average fin pitch Pf2 of the freezing evaporator is Pf1≦Pf2, and the refrigeration evaporator A refrigerator characterized in that a relationship between a height H1 of the container and a height H2 of the freezing evaporator satisfies H1≦H2. 5. The refrigerator according to claim 4 , wherein the defrosting method of the refrigerated storage compartment is an off-cycle defrosting method.

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