JP7063641B2 - refrigerator - Google Patents

Description

The present invention relates to a refrigerator.

As a background technique in this technical field, for example, Japanese Patent Application Laid-Open No. 2006-64256 (Patent Document 1) is available.

In Patent Document 1, the outer shell of the main body is composed of a heat insulating box body, and the internal space (that is, the inside of the refrigerator) of the heat insulating box body is a refrigerating room, an ice room, a select room in which refrigeration or refrigeration can be selected from above. It is equipped with a freezer room and a vegetable room, and the refrigerating room is cooled by the first evaporator, which is an evaporator for the refrigerating room, and the ice room, the select room, and the freezer room are cooled by the second evaporator, which is the evaporator for the freezer room. As the vegetable compartment, a refrigerator that is indirectly cooled by the cooling air of the freezer compartment through a partition wall between the freezer compartment and the like is disclosed (for example, FIG. 3 of Patent Document 1).

Japanese Unexamined Patent Publication No. 2006-64256

The refrigerator described in Patent Document 1 includes a refrigerating room, a freezing temperature zone room (ice room, select room, freezing room), and a vegetable room. The ice chamber, the select chamber, and the freezer compartment are cooled, and the vegetable compartment provided below the freezer compartment is indirectly cooled by the cooling air of the freezer compartment through a partition wall between the ice chamber and the freezer compartment.

When cooling indirectly, it is necessary to promote heat transfer through the partition wall in order to increase the cooling capacity of the vegetable compartment. Generally, in order to promote heat transfer through a partition wall, it is effective to widen the temperature difference between the spaces (freezing room and vegetable room) separated by the partition wall. Therefore, the load on the vegetable compartment is increased due to reasons such as the ambient temperature is high, food with a high temperature is stored in the vegetable compartment, or a gap is created between the vegetable compartment door and the heat insulating box due to sandwiching the food or the like. When it was large and it was necessary to sufficiently increase the cooling capacity, it was necessary to keep the freezing room at an excessively low temperature, resulting in a decrease in cooling efficiency. In addition, the refrigerating room in contact with the freezing room also has a problem that the cooling efficiency is lowered due to the indirect heat influence of the freezing room by keeping the freezing room at an excessively low temperature. That is, there has been a problem that the cooling efficiency of the refrigerator as a whole is lowered because the load of a part of the storage chamber is cooled.

The present invention has been made in view of the above problems, and in a refrigerator provided with a refrigerator compartment, a freezer compartment, and a vegetable compartment, even if the load on some of the storage chambers becomes large, the refrigerator as a whole The purpose is to provide a refrigerator capable of exhibiting high cooling efficiency.

In order to solve the above problems, for example, the configuration described in the claims is adopted.

The present application includes a plurality of means for solving the above problems. For example, the first refrigerating temperature zone chamber, the second refrigerating temperature zone chamber, and the refrigerating temperature zone chamber are provided, and the first refrigerating temperature zone chamber is provided. In a refrigerator equipped with a first evaporator and a first blower on the back of the refrigerator and a second evaporator and a second blower on the back of the refrigerating temperature zone chamber or the second refrigerating temperature zone chamber, by driving the first blower. The first air passage that allows the air that has exchanged heat with the evaporator to flow to the first refrigerating temperature zone chamber, and the air that has exchanged heat with the second evaporator by driving the second blower are sent to the refrigerating temperature zone chamber and the first refrigerating temperature zone chamber. (Ii) A second air passage for circulating in the refrigerating temperature zone chamber is provided, and an air flow blocking means for blocking the flow of air between the first air passage and the second air passage is provided, and the lower part of the first evaporator is provided. Is equipped with a gutter that receives defrost water from the first evaporator and a gutter heater that heats the gutter, and the return air from the first refrigerating temperature zone chamber is applied to the gutter with respect to the first air passage, and at least compressed. By controlling the machine and the first blower, the time average temperature of the first evaporator during the refrigerating operation in the stable cooling operation can be set to the maintenance temperature of the second storage chamber and the maintenance temperature of the first storage chamber. It is characterized in that it is equal to or higher than the arithmetic average value and lower than about -1 ° C.

According to the present invention, in a refrigerator provided with a refrigerator compartment, a freezer compartment, and a vegetable compartment, a refrigerator capable of exhibiting high cooling efficiency as a whole refrigerator even when the load of a part of the storage chamber becomes large is provided. Can be provided.

Front view of the refrigerator according to the embodiment AA sectional view of FIG. BB sectional view of FIG. Schematic diagram showing the air passage configuration of the refrigerator according to the embodiment Schematic diagram showing the refrigerating cycle configuration of the refrigerator according to the embodiment The figure which shows the evaporator of the refrigerator which concerns on Example. Flow chart showing normal operation control of the refrigerator according to the embodiment A flowchart showing the operation control of the refrigerator according to the embodiment when the load is high. An example of a time chart showing normal control of the refrigerator according to the embodiment An example of a time chart showing control of a refrigerator according to an embodiment at a high load. Graph showing the relationship between the evaporator temperature of the refrigerator, the theoretical coefficient of performance, and the temperature of the refrigerator compartment Moriel diagram showing the state of the freezing cycle of the refrigerator

Hereinafter, examples of the present invention will be described in detail with reference to the drawings as appropriate.

Examples of the refrigerator according to the present invention will be described. First, the configuration of the refrigerator according to the embodiment will be described with reference to FIGS. 1 to 5. 1 is a front view of the refrigerator according to the embodiment, FIG. 2 is a sectional view taken along the line AA of FIG. 1, FIG. 3 is a sectional view taken along the line BB of FIG. 2, and FIG. 4 shows an air passage configuration of the refrigerator according to the embodiment. The schematic diagram and FIG. 5 are schematic views showing the configuration of the refrigerating cycle of the refrigerator according to the embodiment. The heat insulating box 10 of the refrigerator 1 is open to the front, and from above, the refrigerating chamber 2 (first refrigerating temperature zone chamber), the ice making chambers 3 arranged side by side on the left and right, the upper freezing chamber 4, and the lower freezing chamber 5, The storage chambers are formed in the order of the vegetable compartment 6 (second refrigerated temperature zone chamber). Hereinafter, the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5 are collectively referred to as a freezing chamber 7 (freezing temperature zone chamber).

The front opening of the refrigerating room 2 is opened and closed by the rotary refrigerating room doors 2a and 2b divided into left and right, and the front opening of the ice making room 3, the upper freezing room 4, the lower freezing room 5, and the vegetable room 6 is. It is opened and closed by a pull-out type ice making room door 3a, an upper freezing room door 4a, a lower freezing room door 5a, and a vegetable room door 6a, respectively. On the outer periphery of the inside of the refrigerator compartment doors 2a and 2b, as seal members, the refrigerator compartment packings 95a and 95b (first seal member), the ice making chamber door 3a, the upper freezer compartment door 4a, and the lower refrigerator compartment door 5a are on the inner periphery of the refrigerator compartment. As a seal member, the freezer compartment packing 96a, 96b, 96c (second seal member), and the vegetable compartment packing 97 (third seal member) as a seal member on the inner periphery of the inside of the vegetable compartment door 6a, which is the door of the vegetable compartment 6. ), And when each door is closed, it comes into contact with the front edge of the heat insulating box 10 to suppress the flow of air inside and outside the refrigerator. The peripheral lengths of the refrigerating chamber packings 95a and 95b are 2271 mm and 2441 mm, respectively, and the total peripheral lengths of the refrigerating chamber packings 95a and 95b (peripheral length of the first seal member) are 4712 mm. The peripheral lengths of the freezing chamber packings 96a, 96b and 96c are 976 mm, 1416 mm and 2087 mm, respectively, and the total peripheral lengths of the freezing chamber packings 96a, 96b and 96c (the peripheral length of the second seal member) are 4209 mm. The circumference of the vegetable compartment packing 97 (perimeter of the third seal member) is 2107 mm. The open / closed states of the refrigerating room doors 2a and 2b, the ice making room door 3a, the upper freezing room door 4a, the lower freezing room door 5a, and the vegetable room door 6a are in close proximity to each door and the front edge of the heat insulating box 10. Is detected by a door sensor (not shown).

Door hinges (not shown) are provided at the upper and lower parts of the refrigerator compartment 2 to fix the refrigerator 1 and the doors 2a and 2b, and the upper door hinges are covered with the door hinge cover 16. Further, the door 2a is provided with an operation unit 99 for operating the temperature setting in the refrigerator.

The temperature of the refrigerating chamber 2 and the temperature of the freezing chamber 7 can be selected by the user via the operation unit 99. Specifically, the maintenance temperature levels of the refrigerating room 2 and the freezing room 7 can be set in three stages of "strong", "medium", and "weak", respectively, and the refrigerating room 2 is about "strong". It is maintained at 2 ° C, about 4 ° C at "medium", about 6 ° C at "weak", about -22 ° C at "strong", about -20 ° C at "medium", and about-about-at "weak". It is maintained at 18 ° C. The vegetable compartment 6 is maintained at about 7 ° C. on average.

The width W of the refrigerator 1 is W = 685 mm (see FIG. 1), the depth D is D = 738 mm (see FIG. 2), and the height H is H = 1833 mm (see FIG. 1). The refrigerator compartment height dimension _HR is _HR = 787 mm, the freezer chamber height dimension _HF is _HF = 482 mm, and the vegetable compartment height dimension _HV is _HV = 334 mm (see FIG. 2). The total rated internal volume based on JISC9801-3: 2015 is 602L, and the breakdown is that the rated internal volume of the refrigerating chamber 2 (rated internal volume of the refrigerating chamber) is 308L, which is 51.2% of the total rated internal volume of the freezer compartment 7. The rated internal volume (rated internal volume of the freezer room) is 180 L, which is 29.9% (28% or more of the total rated internal volume), and the rated internal volume of the vegetable room 6 (rated internal volume of the vegetable room) is 114 L, which is the total rated content. It is 18.9% of the product.

As shown in FIG. 2, the outside and inside of the refrigerator 1 are separated by a heat insulating box 10 formed by filling an outer box 10a and an inner box 10b with a foamed heat insulating material (for example, urethane foam). ing. In the heat insulating box body 10, in addition to the foam heat insulating material, a plurality of vacuum heat insulating materials 36 are mounted between the outer box 10a made of steel plate and the inner box 10b made of synthetic resin. The refrigerating room 2, the upper freezing room 4, and the ice making room 3 are separated by a heat insulating partition wall 28 (air flow blocking means), and the lower freezing room 5 and the vegetable room 6 are separated by a heat insulating partition wall 29. Further, on the front side of each storage chamber of the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5, a heat insulating partition wall is provided to prevent the flow of air inside and outside the refrigerator through the gaps between the doors 3a, 4a, and 5a. 30 is provided.

A plurality of door pockets 33a, 33b, 33c opened upward and a plurality of shelves 34a, 34b, 34c, 34d are provided inside the doors 2a, 2b of the refrigerating chamber 2, and are partitioned into a plurality of storage spaces. .. The opening height (broken line in FIG. 2) of the uppermost door pocket 33a is provided at a position higher than that of the uppermost shelf 34a. In the freezing room 7 and the vegetable room 6, an ice making room container (not shown), an upper freezing room container 4b, a lower freezing room container 5b, and a vegetable room container 6b, which are drawn out integrally with the doors 3a, 4a, 5a, 6a, respectively, are provided. I have. The vegetable compartment container 6b is divided into upper and lower tiers, and is provided with a bottle storage space 6c in front of the lower tier for storing beverage bottles. The height dimension of the bottle storage space 6c is secured to be 305 mm or more so that 1.5 L or 2 L beverage bottles can be stored upright (315 mm in this embodiment). In addition, the fact that bottles for beverages can be stored is made known to users through catalogs, instruction manuals, texts such as advertising media, figures, photographs, and videos.

Above the heat insulating partition wall 28, a chilled room 35 that can be set lower than the temperature zone of the refrigerating room 2 is provided. In the chilled room 35, the user can select the set temperature via the operation unit 99. Specifically, it can be set to either "temperature level 1" that maintains the refrigerating temperature range at about 0 to 3 ° C. or "temperature level 2" that maintains the refrigerating temperature range at about -3 to 0 ° C. can.

An ice-making water tank (not shown) is provided on the left side of the chilled room 35. A water pump (not shown) is provided on the back of the ice-making water tank. Further, the ice water tank, the water supply pump, and the water supply pump are connected by a water supply pipe (not shown) to the upper part of the ice tray (not shown) in the ice making chamber 3 through the heat insulating partition wall 28. Water can be supplied from the ice-making water tank to the ice-making tray by driving the water supply pump. The ice tray is connected to an ice-removing mechanism (not shown), and the operation of the ice-removing mechanism causes ice to fall from the ice tray into the ice-making chamber container. The user can select ON / OFF of the automatic ice making function via the operation unit 99, and when the automatic ice making function is turned on, the water in the ice making water tank is periodically driven by the water supply pump to make an ice tray. Water is supplied to the ice tray, and after a predetermined time has passed, the ice removal mechanism is automatically activated and ice falls into the ice making chamber container.

A refrigerating evaporator chamber 8a is provided substantially at the back of the refrigerating chamber 2, and a refrigerating evaporator 14a (first evaporator), which is a fin tube type heat exchanger, is housed in the refrigerating evaporator chamber 8a. Has been done. A refrigerating fan 9a (first blower) is provided above the refrigerating evaporator 14a. Further, a refrigerating chamber air passage 11 is provided at substantially the center of the back of the refrigerating chamber 2 in the width direction, and a refrigerating chamber discharge port provided with a directing means for directing the blown air upward at the upper portion of the refrigerating chamber air passage 11. It is equipped with 11a. In the refrigerator of this embodiment, the opening surface of the refrigerating chamber discharge port 11a is directed upward as a directing means of the refrigerating chamber discharge port 11a. The cooling air blown upward from the refrigerating chamber discharge port 11a flows along the ceiling surface of the refrigerating chamber 2 as shown by an arrow in FIG. 2, reaches the area in front of the refrigerating chamber 2, and reaches the area in front of the refrigerating chamber 2 and reaches the shelf 34a. , 34b, 34c, flow through the gap between the door pockets 33a, 33b, 33c, and the chilled room 35 through the opening 92 (see FIG. 3) provided at the left rear of the space between the shelves 34c and the shelves 34d. From the refrigerating chamber return air passages 15a, 15b, 15c (see FIG. 3) provided on the lower front surface, the lower left side surface, and the lower right front surface of the refrigerating evaporator chamber 8a to the refrigerating evaporator chamber 8a. return. Further, a part of the air flowing through the space between the shelves 34c and the shelves 34d is for refrigerating from the refrigerating chamber return air passage 15d (see FIG. 3) provided at the right rear of the space between the shelves 34c and the shelves 34d. Return to the evaporator chamber 8a. A part of the refrigerating chamber return air passage 15c is provided with a deodorizing member 91 (as an example, an open cell structure deodorizing member) so as to be in contact with the air flowing through the refrigerating chamber 2.

A freezing evaporator chamber 8b is provided substantially at the back of the freezing chamber 7, and a freezing evaporator 14b (second evaporator), which is a fin tube type heat exchanger, is housed in the freezing evaporator chamber 8b. Has been done. A freezing fan 9b is provided above the freezing evaporator 14b. Further, the back of the freezing chamber 7 is provided with a freezing chamber air passage 12, and the freezing chamber air passage 12 in front of the freezing fan 9b (second blower) is provided with a plurality of freezing chamber discharge ports 12a. A freezing chamber return air passage 17 (see FIGS. 2 and 3) for returning air sent to the freezing chamber 7 is provided in front of the lower part of the freezing chamber evaporator chamber 8b.

The vegetable compartment air passage 13 serving as an air passage to the vegetable chamber 6 is branched from the lower right of the freezing chamber air passage 12 and passes through the heat insulating partition wall 29. The vegetable compartment discharge port 13a, which is the outlet of the vegetable compartment air passage 13, is provided so as to substantially coincide with the height of the lower surface of the heat insulating partition wall 29 on the upper right of the back of the vegetable chamber 6 and opens downward. The vegetable compartment air passage 13 is provided with a vegetable compartment damper 19 which is a cooling control means for the vegetable compartment 6 (see FIG. 3). A vegetable compartment return inlet 18a is provided in front of the lower left of the heat insulating partition wall 29 between the vegetable compartment 6 and the freezing chamber 7, and is frozen via the vegetable compartment return air passage 18 passing through the heat insulating partition wall 29. A flow path leading to the return outlet 18b of the vegetable chamber provided in front of the lower part of the evaporator chamber 8b is formed.

Next, the air passage configuration of the refrigerator according to this embodiment will be described with reference to FIG. The air that has become cold due to heat exchange with the refrigerating evaporator 14a is blown to the refrigerating chamber 2 through the refrigerating chamber air passage 11 and the refrigerating chamber discharge port 11a by driving the refrigerating fan 9a. 2 Cool the inside. The air sent to the refrigerating chamber 2 returns to the refrigerating evaporator chamber 8a from the refrigerating chamber return air passages 15a, 15b, 15c and 15d (see FIG. 3). Hereinafter, the air passage that flows from the refrigerating evaporator chamber 8a through the refrigerating chamber 2 and returns to the refrigerating evaporator chamber 8a is referred to as a refrigerating air passage 111 (first air passage). Further, the air that has become cold due to heat exchange with the freezing evaporator 14b is blown to the freezing chamber 7 through the freezing chamber air passage 12 and the freezing chamber discharge port 12a by driving the freezing fan 9b. The inside of the freezing chamber 7 is cooled. The air sent to the freezing chamber 7 returns from the freezing chamber return air passage 17 to the freezing evaporator chamber 8b. When the vegetable compartment damper 19 is in the open state, a part of the cooling air flowing into the freezing chamber air passage 12 flows through the vegetable chamber air passage 13 and reaches the vegetable chamber 6 via the vegetable chamber discharge port 13a. Cool the inside of the vegetable compartment 6. The air sent to the vegetable compartment 6 flows through the vegetable compartment return air passage 18 and returns to the freezing evaporator chamber 8b. Hereinafter, the air passage that flows from the freezing evaporator chamber 8b through the freezing chamber 7 and returns to the freezing evaporator chamber 8b, and the wind that flows from the freezing evaporator chamber 8b through the vegetable chamber 6 and returns to the freezing evaporator chamber 8b. The road is called a frozen vegetable air passage 112 (second air passage).

In the refrigerator of this embodiment, the refrigerating fan 9a is a centrifugal fan (rearward fan) having a blade diameter of 100 mm, and the refrigerating fan 9b is an axial flow fan (propeller fan) having a blade diameter of 110 mm. The centrifugal fan has the property of turning the air sucked in from the axial direction by 90 degrees and blowing it out in the radial direction. On the other hand, the axial flow fan has the characteristic of blowing out the air sucked from the axial direction in the axial direction. Therefore, the centrifugal fan is excellent in mountability in the air passage that diverts the flow sucked in the axial direction by 90 degrees, and the axial flow fan is excellent in the mountability in the air passage that blows out the flow sucked in the axial direction in the axial direction. Therefore, the refrigerating fan 9a has a configuration in which the air sucked from the front is turned 90 degrees and blown out to the upper refrigerating chamber air passage 11. Therefore, a rearward fan, which is a centrifugal fan, is adopted as the refrigerating fan 9b. Is a refrigerator with high space efficiency by adopting a propeller fan, which is an axial fan, because the air sucked from the rear is blown out to the air passage 12 in the freezer compartment in the front.

As shown in FIGS. 2 and 3, on the back side of the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6, the refrigerator compartment temperature sensor 41 (first load detecting means) and the freezer compartment temperature sensor 42 (second). A load detecting means) and a vegetable room temperature sensor 43 are provided, and the temperatures of the refrigerating room 2, the freezing room 7, and the vegetable room 6 are detected, respectively. Further, a refrigerating evaporator temperature sensor 40a is provided above the refrigerating evaporator 14a, and a refrigerating evaporator temperature sensor 40b is provided above the refrigerating evaporator 14b, and the refrigerating evaporator 14a and the refrigerating evaporator 14b are provided. The temperature of is detected. Further, inside the door hinge cover 16 on the ceiling of the refrigerator 1, an outside air temperature / humidity sensor 37 for detecting the temperature and humidity of the outside air (outside air) is provided, and the doors 2a, 2b, 3a, 4a, 5a, 6a are provided. Is equipped with a door sensor (not shown) that detects the open / closed state.

Further, a defrost heater 21 for heating the freezing evaporator 14b is provided in the lower part of the freezing evaporator chamber 8b. The defrost heater 21 is, for example, an electric heater of 50 W to 200 W, and in this embodiment, a radiant heater of 150 W is provided. The defrosted water (melted water) generated during the defrosting of the refrigerating compressor 14b flows down to the trough 23b provided in the lower part of the refrigerating evaporator chamber 8b, and flows down to the refrigerator via the drain port 22b and the refrigerating drain pipe 27b. It reaches the machine chamber 39 provided in the lower part behind (rear side) of No. 1, and is discharged to the evaporation tray 32 in the upper part of the compressor 24 installed in the machine chamber 39.

The method for defrosting the refrigerating evaporator 14a will be described later, but the defrosting water generated during the defrosting of the refrigerating evaporator 14a flows down to the trough 23a provided in the lower part of the refrigerating evaporator chamber 8a. It is discharged to the evaporator 32 provided in the upper part of the compressor 24 via the drain port 22a and the refrigerating drain pipe 27a.

In the machine room 39, along with the compressor 24 and the evaporating dish 32 described above, a fin tube type heat exchanger, an outside radiator 50a, and an outside fan 26 are provided. By driving the outside fan 26, air flows through the compressor 24 and the outside radiator 50a evaporating dish 32, promoting heat dissipation from the compressor 24 and the outside radiator 50a, improving energy saving performance and making the evaporating dish 32. By ventilating, the evaporation of the defrosted water accumulated in the evaporating dish 32 is promoted, the overflow is suppressed, and the reliability is improved.

As shown in FIG. 3, the gutter 23a is provided with a gutter heater 101 that melts the defrosted water frozen in the gutter 23a. Further, the drainage pipe 27a for refrigeration is provided with a drainage pipe upper heater 102 and a drainage pipe lower heater 103. The gutter heater 101, the drain pipe upper heater 102, and the drain pipe lower heater 103 are all heaters having a lower capacity than the defrost heater 21, and in this embodiment, the gutter heater 101 is 6 W and the drain pipe upper heater 102 is used. 3W, the drainage pipe lower heater 103 is 1W.

Here, when the refrigerating fan 9a is driven, the return air from the refrigerating chamber 2 is flowed downward toward the gutter 23a through the refrigerating chamber return port 15b provided in the upper right of the refrigerating evaporator chamber 8a, and the gutter is used. 23a is heated to raise the temperature. As a result, the effect of reducing the heating amount of the gutter heater 101 that melts the frozen defrost water in the gutter 23a can be obtained, and the energy saving performance can be improved.

Further, the lower part of the drain pipe 27a is closer to the outer box 10a than the freezing chamber 7 and the freezing evaporator chamber 8b. As a result, the amount of heat of the drainage pipe lower heater 103 that melts the frozen defrosted water in the drainage pipe 27a can be reduced, and the energy saving performance is improved.

On the ceiling of the refrigerator 1 (see FIG. 2), a control board 31 on which a CPU, a memory such as a ROM or RAM, an interface circuit, etc., which are a part of the control device, is arranged is arranged. The control board 31 is connected to the refrigerating room temperature sensor 41, the freezing room temperature sensor 42, the vegetable room temperature sensor 43, the evaporator temperature sensors 40a, 40b, etc., and the CPU described above sets these output values and the operation unit 99. , ON / OFF and rotation speed control of compressor 24, refrigerating fan 9a, refrigerating fan 9b, defrost heater 21, gutter heater 101, drain pipe upper heater, based on the program recorded in advance in the above-mentioned ROM. It controls 102, the drain pipe lower heater 103, and the three-way valve 52, which will be described later.

FIG. 5 is a refrigerating cycle (refrigerant flow path) of the refrigerator according to the first embodiment. In the refrigerator 1 of this embodiment, the compressor 24 (pressing amount 9.2 cc), the outside radiator 50a for radiating the refrigerant, the wall surface heat radiating pipe 50b, and the front edges of the heat insulating partition walls 28, 29, 30 are provided. A dew condensation suppressing pipe 50c that suppresses dew condensation (external radiator 50a, an external radiator 50b, and a dew condensation suppressing pipe 50c are called heat dissipation means), a three-way valve 52 that is a refrigerant flow control means, and a decompression means that reduces the pressure of the refrigerant. It includes a refrigerating capillary tube 53a, a refrigerating capillary tube 53b, a refrigerating evaporator 14a that absorbs heat in the refrigerator by exchanging heat between the refrigerant and the air in the refrigerator, and a refrigerating evaporator 14b. Further, a dryer 51 for removing water during the refrigeration cycle is provided upstream of the three-way valve 52, and liquid refrigerant is supplied to the compressor 24 downstream of the refrigerating evaporator 14a and downstream of the refrigerating evaporator 14b, respectively. It is provided with a refrigerating gas-liquid separator 54a and a refrigerating gas-liquid separator 54b for preventing inflow. Further, a check valve 56 is provided downstream of the freezing gas-liquid separator 54b. A refrigeration cycle is configured by connecting these components with a refrigerant pipe. In the refrigerator of this embodiment, the temperature of the refrigerating evaporator 14a and the refrigerating evaporator 14b is adjusted by the rotation speeds of the compressor 24, the refrigerating fan 9a, and the refrigerating fan 9b, so that the compressor 24 and the refrigerator are refrigerated. The fan 9a for refrigeration and the fan 9b for refrigeration are called an evaporator temperature adjusting means. Further, isobutane, which is a flammable refrigerant, is used as the refrigerant, and the amount of the refrigerant enclosed is 88 g.

The three-way valve 52 includes an outlet 52a and an outlet 52b, with the outlet 52a open and the outlet 52b closed, and a state 1 (refrigerating mode) in which the refrigerant flows to the refrigerating capillary tube 53a side. With the outlet 52a closed and the outlet 52b open, the refrigerant flows to the refrigerating capillary tube 53b side (freezing mode), and both the outlets 52a and 52b are closed 3 (all). It is a refrigerant flow control valve equipped with a closed mode).

When the three-way valve 52 is controlled to the state 1 (refrigerating mode), the refrigerant discharged from the compressor 24 flows through the outside radiator 50a, the outside radiator 50b, and the dew condensation suppression pipe 50c to dissipate heat, and the dryer 51. It reaches the three-way valve 52 via. Since the three-way valve 52 is in the state 1 (the outflow port 52a is in the open state and the outflow port 52b is in the closed state), the refrigerant subsequently flows through the refrigerating capillary tube 53a and is depressurized to reach the refrigerating evaporator 14a. It exchanges heat with the return air of the refrigerator compartment 2. The refrigerant leaving the refrigerating evaporator 14a passes through the refrigerating gas-liquid separator 54a, flows through the contact portion 57a with the capillary tube 53a, exchanges heat with the refrigerant flowing in the capillary tube 53a, and then returns to the compressor 24. ..

When the three-way valve 52 is controlled to the state 2 (refrigeration mode), the refrigerant discharged from the compressor 24 flows through the outside radiator 50a, the outside radiator 50b, and the dew condensation suppression pipe 50c to dissipate heat, and the dryer 51. It reaches the three-way valve 52 via. Since the three-way valve 52 is in the state 2 (the outflow port 52a is in the closed state and the outflow port 52b is in the open state), the refrigerant subsequently flows through the refrigerating capillary tube 53b and is depressurized to lower the temperature, and the refrigerating evaporator At 14b, heat is exchanged with the return air of the freezing chamber 7 and the return air of the vegetable compartment 6 (when the vegetable compartment damper 19 is in the open state). The refrigerant leaving the freezing evaporator 14b passes through the freezing gas-liquid separator 54b, flows through the contact portion 57b with the capillary tube 53b, exchanges heat with the refrigerant flowing in the capillary tube 53b, and then returns to the compressor 24. ..

When the three-way valve 52 is controlled to the state 3 (fully closed mode), when the compressor 24 is driven, the refrigerant is not supplied from the refrigerating capillary tube 53a and the refrigerating capillary tube 53b, so that the refrigerating evaporator The refrigerant in 14a or the refrigerant in the refrigerating evaporator 14b is recovered on the heat radiating means side (details will be described later).

In the refrigerator of this embodiment, the three-way valve 52 is controlled to the state 1 (refrigerating mode), the compressor 24 is driven, the refrigerating fan 9a is driven, and the refrigerating fan 9b is stopped. "Refrigerating operation", the three-way valve 52 is controlled to state 2 (refrigerating mode), the compressor 24 is in the driving state, the vegetable compartment damper 19 is in the open state, the refrigerating fan 9a is in the driving state, or stopped, and refrigerated. "Frozen vegetable operation" that cools the freezer compartment 7 and the vegetable compartment 6 by driving the fan 9b, controls the three-way valve 52 to the state 2 (freezing mode), drives the compressor 24, and the vegetable compartment damper. 19 is in the closed state, the refrigerating fan 9a is in the driving state or stopped state, the refrigerating fan 9b is in the driving state to cool the freezing chamber 7, and the three-way valve 52 is in the state 3 (fully closed mode). "Refrigerator recovery operation" in which the refrigerant in the refrigerating evaporator 14a or the refrigerant in the refrigerating evaporator 14b is recovered to the heat dissipation means side by controlling and driving the compressor 24, and the three-way valve 52 is in the state 3 (state 3 ( Fully closed mode), the compressor 24 is stopped, the refrigerating fan 9a is stopped, the refrigerating fan 9b is stopped, the three-way valve 52 is in state 2 (refrigerating mode), and the compressor 24 is driven. Refrigerate with the refrigerating fan as the driving state so that the refrigerant does not flow to the refrigerating evaporator 14a by controlling the state or controlling the three-way valve 52 to the state 3 (fully closed mode) and the compressor 24 to the stopped state. "Refrigerator evaporator defrosting operation" that defrosts the refrigerating evaporator 14a while cooling the refrigerating chamber 2 with the frost grown on the surface of the refrigerating evaporator 14a and the cold storage heat of the refrigerator itself, the three-way valve 52 is in a state. By setting the compressor 24 to the stopped state, the refrigerating fan 9a to the driving state or the stopped state, the refrigerating fan 9b to the stopped state, and the defrost heater 21 to be energized as 3 (fully closed mode), the refrigerating evaporator 14b By appropriately performing each operation of the "refrigerator evaporator defrosting operation" for defrosting, each storage room in the refrigerator 1 is cooled.

The interval at which the refrigerating evaporator defrosting operation is performed (defrosting interval) is variable between a maximum of 96 hours (maximum defrosting interval) and a minimum of 12 hours (shortest defrosting interval). Specifically, the outside temperature / humidity detected by the outside temperature / humidity sensor 37, the number of times the doors 3a, 4a, 5a, and 6a are opened / closed, the compressor rotation speed during the freezing operation and the frozen vegetable operation, and the refrigerating evaporator temperature sensor 40b. The defrosting interval is determined based on the detected freezing evaporator temperature, and the outside air temperature is high, the outside air humidity is high, the freezing room door is opened and closed frequently, and the compressor rotation speed during freezing operation and frozen vegetable operation is high. The higher the minimum temperature reached for the freezing evaporator during freezing operation and frozen vegetable operation, the shorter the interval. By varying the interval of the refrigerating evaporator defrosting operation in this way, when frost grows on the refrigerating evaporator 14b, the refrigerating evaporator defrosting operation can be performed at an appropriate timing, so that the frost is excessive. It suppresses the heat exchange efficiency of the refrigerating evaporator from dropping significantly, and makes it possible to demonstrate good practical cooling performance. In addition, by setting the longest defrosting interval, reliable freezing evaporator defrosting operation is performed on a regular basis. As a result, the growth of unintended frost on the wall surface of the freezing evaporator chamber 8b other than the freezing evaporator 14b can be suppressed, and the reliability is improved. Further, during the freezing evaporator defrosting operation, the temperature of the freezing chamber 7 rises because the freezing chamber 7 cannot be cooled. In the refrigerator of this embodiment, the shortest defrosting interval is provided to prevent the defrosting interval from becoming too short, and the temperature of the freezing chamber 7 is prevented from rising frequently due to the defrosting operation, so that the frozen food can be thawed. It is a refrigerator that is unlikely to malfunction.

When the refrigerant in the refrigerating evaporator 14a is recovered to the heat radiating means side, the refrigerating fan 9a is driven, and when the refrigerant in the refrigerating evaporator 14b is recovered to the radiating means side, the refrigerating fan 9a is driven. The fan 9b is driven to cool the refrigerating chamber 2 and the freezing chamber 7 even during the refrigerant recovery operation (details will be described later). Therefore, the general term for the "refrigerating operation", which is the operation state in which the refrigerating chamber 2 is cooled, and the refrigerant recovery operation, which recovers the refrigerant in the refrigerating evaporator 14a, is "refrigerating chamber cooling operation", and the refrigerating chamber 7 is cooled. The general term for "frozen vegetable operation" and "freezing operation", which are in the operating state, and the refrigerant recovery operation for recovering the refrigerant in the refrigerating evaporator 14b is called "freezer compartment cooling operation".

6A and 6B are views showing an evaporator of a refrigerator according to this embodiment, FIG. 6A is a refrigerating evaporator 14a, and FIG. 6B is a freezing evaporator. As shown in FIG. 6A, the refrigerating evaporator 14a is a fin tube type heat exchanger in which aluminum fins 98a are attached to an aluminum refrigerant pipe 97a. Refrigerant that has been decompressed by the refrigerating capillary tube 53a (see FIG. 5) and has become low temperature and low pressure flows through the refrigerant pipe 97a and returns air from the refrigerating chamber 2 (FIG. 2 or 2) that flows in from the lower front of the refrigerating evaporator 14a. (See FIG. 3) and heat exchanges with the fins 98a and the surface of the refrigerant pipe 97a. The fin 98a is divided into three stages in the height direction, and each stage is provided with two rows of front and rear refrigerant pipes 97a. The refrigerant flows in from the refrigerant pipe 97a behind the upper part of the refrigerating evaporator 14a, faces downward on the right side of the refrigerating evaporator 14a, and flows into the rear of the first stage of the fin 98a. After that, it flows in the order of the second stage rear, the third stage rear, the third stage front, the second stage front, and the first stage front, and flows out from the right side of the first stage. A refrigerating gas-liquid separator 54a connected to the refrigerant pipe 97a is provided on the right side of the refrigerating evaporator 14a so that the liquid refrigerant and the gas refrigerant are separated. Further, a refrigerating evaporator temperature sensor 40a is attached to a refrigerant pipe above and behind the refrigerating evaporator 14a by a sensor holder (not shown). The width W _Revp = 300 mm, depth D _Revp = 60 mm, height H _Revp = 88 mm of the part (fin installation part) where the fin 98a where the main heat exchange is performed is installed in the refrigerating evaporator 14a, and the fin is installed. Occupied volume of part (volume of evaporator for refrigeration) V _Revp = 1.486L. Further, the fin pitch Pf _Revp = 3 mm. The surface area (heat transfer area on the air side) A _Revp of the fin 98a of the fin installation portion and the refrigerant pipe 97a in contact with air is 0.993 m ² .

FIG. 6B is a refrigerating evaporator 14b, which is a fin tube type heat exchanger in which aluminum fins 98b are attached to an aluminum refrigerant pipe 97b. Refrigerant that has been decompressed by the refrigerating capillary tube 53b (see FIG. 5) and has become low temperature and low pressure flows through the refrigerant pipe 97b and flows in from the lower front of the refrigerating evaporator 14b. (See FIG. 2 or FIG. 3) and heat exchange through the surfaces of the fins 98b and the refrigerant pipe 97b. The fins 98b are divided into five stages in the height direction of the refrigerating evaporator 14b, and each stage is provided with two rows of front and rear refrigerant pipes 97b. The refrigerant flows in from the refrigerant pipe 97b in front of the upper part of the refrigerating evaporator 14a, and flows in front of the fifth stage of the fin 98a. After that, it flows in the order of 4th stage front, 3rd stage front, 2nd stage front, 1st stage front, 1st stage rear, 2nd stage rear, 3rd stage rear, 4th stage rear, and 5th stage rear. ， It flows out from the upper left behind the 5th stage. On the upper left side of the refrigerating evaporator 14b, a refrigerating gas-liquid separator 54b connected to the refrigerant pipe 97b is provided at an angle (15 degrees) with respect to the vertical line, and is provided with a liquid refrigerant and a gas refrigerant. Is designed to be separated. Further, a freezing evaporator temperature sensor 40b is attached to a refrigerant pipe in front of the upper part of the freezing evaporator 14a by a sensor holder (not shown). The width of the part (fin installation part) where the fins 98b where the main heat exchange is performed in the refrigerating evaporator 14b is installed is W _Febp 1 = 345 mm in the first to fourth stages and W _Febp in the fifth stage. 2 = 300 mm, depth D _Fevp = 60 mm, height of the first to fourth steps _Evapor1 = 118 mm, height of the fifth step H _evapor1 = 30 mm. The occupied volume of the fin installation portion (volume of the evaporator for freezing) determined from these is V _Fevp = 2.983 L, which is 3% or less of the rated internal volume of the freezer chamber 7 of 180 L. By setting the volume of the evaporator for freezing to 3% or less of the rated internal volume of the freezing chamber 7 in this way, the rated internal volume of the freezing chamber 7 can be increased to 28% or more of the total rated internal volume. Further, the fin pitch Pf _Febp = 5 mm, and the surface area (air side heat transfer area) of the fin 98b of the fin installation portion and the refrigerant pipe 97b in contact with air is A _Febp = 1.146 m ² .

The heat transfer areas on the air side per unit volume of the refrigerating evaporator 14a and the refrigerating evaporator 14b shown in FIG. 6 are A _Revp / V _Revp = 0.673m ² / L and A _Fevp / V _Febp = 0, respectively. It is 384 m ² / L, which is a value of 0.25 m ² / L or more and 0.96 m ² / L or less. In general, frost grows on the air-side heat transfer surface of the evaporator, so if the air-side heat transfer area is increased relative to the evaporator volume, the flow path is likely to be blocked when frost grows. Therefore, when the frost growth is large, the heat exchange performance is likely to deteriorate, but when the frost growth is small, the evaporator has high heat exchange performance. On the other hand, if the heat transfer area on the air side is made smaller than the volume of the evaporator, the flow path is less likely to be blocked by the frost even if frost grows, and it becomes easier to maintain heat exchange performance, but the heat transfer area on the air side becomes smaller. ， When the growth of frost is small, the heat exchange performance per unit volume becomes low. Therefore, in the refrigerator of this embodiment, the heat transfer area on the air side per unit volume of the refrigerating evaporator 14a and the refrigerating evaporator 14b shall be 0.25 m2 / L or more and 0.96 m2 / L or less. Therefore, the performance is compatible between the case where the frost growth is large and the case where the frost growth is small.

The configuration of the refrigerator according to this embodiment has been described above. Next, the control of the refrigerator according to this embodiment will be described. FIG. 7 is a flowchart showing the control of the refrigerator according to the present embodiment in the normal operating state. FIG. 8 is a flowchart showing the control of the refrigerator according to the present embodiment in a high load state. FIG. 9 is a time chart showing control of the refrigerator according to the present embodiment in a normal operating state. FIG. 10 is a time chart showing control in a high load state of the refrigerator according to this embodiment.

As shown in FIG. 7, the refrigerator of this embodiment is started to operate by turning on the power (start), and each storage chamber of the refrigerator 1 is cooled. In the normal operation state (normal operation mode) where the user opens and closes each storage room door or there is no load fluctuation due to factors such as changes in the temperature environment around the refrigerator, basically a constant operation pattern is repeated (hereinafter). , Called stable cooling operation). In FIG. 5, the control process from turning on the power to the stable cooling operation is omitted.

In the stable cooling operation, a constant operation pattern (operation cycle) is repeated, but here, control from a state in which the refrigerating operation, which is an operation mode for cooling the refrigerating chamber 2, is started, will be described. In the refrigerating operation, the three-way valve 52 is set to state 1 (refrigerating mode), the compressor 24 is driven at a speed of 1 (800min ^-1 ), the refrigerating fan 9a is driven at a speed of 2 (1500min ^-1 ), and the refrigerating fan 9b is driven. It starts by stopping and closing the vegetable compartment damper 19 (step S101). Subsequently, it is determined whether or not the inside of the refrigerator has a high load (step S102). In the refrigerator of this embodiment, the freezing room temperature T _F detected by the freezing room temperature sensor 42 is a high load determination temperature T _{F_high} (= -10 ° C.) or higher ( _TF ≧ T _{F_high} ), or the refrigerating room temperature sensor 41. Step S102 is established when the refrigerating room temperature TR detected by is _{equal to or higher than the high load determination temperature TR_high (} = 10 ° C.) ( _{TR ≧ TR_high )} . The control when step S102 is established will be described later.
At this time, the compressor 24 and the refrigerating fan 9a have T _{Revp_ave} as the time average temperature of the refrigerating evaporator 14a during the refrigerating operation, _{TF_keep} as the maintenance temperature of the refrigerating chamber 2, and _{TF_keep} as the maintaining temperature of the refrigerating chamber 7. When the difference between the refrigerating room maintenance temperature T _{R_keep} and the time average temperature T _{Revp_ave} of the refrigerating evaporator 14a during refrigerating operation is ΔT (= T _{R_keep} －T _{Revp_ave} ), and the refrigerating cycle theoretical coefficient of performance for the evaporator temperature is COP _th . In addition, T _{Revp_ave} ≧ 0.5 × (T _{R_keep} + T _{F_keep} ), d ² (COP _th ) / dT _{Revp_ave} ² -d ² (ΔT ^-1 ) / dT _{Revp_ave} ² ≧ 0 are selected to be satisfied.

If step S102 is not satisfied (No), it is subsequently determined whether the refrigerating operation end condition is satisfied (step S103). In the refrigerator of this embodiment, step S103 is established when the refrigerating room temperature TR detected by the refrigerating room temperature sensor 41 is the refrigerating operation end temperature _TRoff (= 2.5 ° C.) or less ( _TR ≤ _TRoff ) _. do. If step S103 is not established (No), the process returns to the determination in step S102 again.

When step S103 is satisfied (Yes), it is determined whether or not the frozen vegetable operation start condition is satisfied (step S104). In the refrigerator of this embodiment, step S104 is established when the freezing room temperature _TF detected by the freezing room temperature sensor 42 is equal to or higher than the frozen vegetable operation start temperature _{TF_on} (= -18 ° C.) ( _TF ≧ _{TF_on} ). do.

If step S104 is established (if not established (No) will be described later), then the drive rotation speed of the compressor 24 is maintained, the three-way valve 52 is set to state 3 (fully closed mode), and the inside of the refrigerating evaporator 14a. A refrigerant recovery operation is performed to recover the refrigerant of the above to the heat dissipation means side (step S105). At this time, the refrigerating fan 9a continues to be driven and cools the refrigerating chamber 2 even during the refrigerant recovery operation.

Subsequently, it is determined whether to carry out the refrigerating evaporator defrosting operation (step S106). In the refrigerator of this embodiment, if the setting of the chilled room 35 provided in the lower part of the refrigerating chamber 2 is "temperature level 1" for maintaining the temperature at about 0 to 3 ° C. in the refrigerating temperature range, step S106 is performed. If “Yes” and “Temperature level 2” that maintains the temperature in the freezing temperature range of about -3 to 0 ° C. is selected, step S106 is rejected (No). When step S106 is established (Yes), the refrigerating fan 9a is set to a speed of 1 (900min ^-1 ), the refrigerating evaporator defrosting operation is started (step S107), and when step S106 is rejected (No). The refrigerating fan 9a is stopped (step S108).

Next, the frozen vegetable operation is started (step S109). In the frozen vegetable operation, the three-way valve 52 is set to state 2 (freezing mode), the compressor 24 is driven at a speed of 2 (1400 min ^-1 ), the freezing fan 9b is driven at a speed of 1 (1200 min ^-1 ), and the vegetable compartment damper 19 is operated. It is done in an open state.

Subsequently, it is determined whether or not the inside of the refrigerator has a high load (step S110). In the refrigerator of this embodiment, the freezing room temperature T _F detected by the freezing room temperature sensor 42 is a high load determination temperature T _{F_high} (= -10 ° C.) or higher ( _TF ≧ T _{F_high} ), or the refrigerating room temperature sensor 41. Step S110 is established when the refrigerating room temperature TR detected by is _{equal to or higher than the high load determination temperature TR_high (} = 10 ° C.) ( _{TR ≧ TR_high )} (determination similar to step S102). The control when step S110 is established will be described later.
If step S110 is not satisfied (No), then it is determined whether the vegetable room cooling end condition is satisfied (step S111). In the refrigerator of this embodiment, step S111 is established when the vegetable room temperature _{TV detected by the vegetable room temperature sensor 43 is not more than or equal to the vegetable room cooling end temperature TV_off (} = 4 ° C.) ( _{TV ≤ TV_off )} . .. When step S111 is established (Yes), the vegetable compartment damper 19 is closed, the frozen vegetable operation ends, and the freezing operation shifts to cooling the freezing chamber 7.

If step S111 is not satisfied (No), it is subsequently determined whether the refrigerating evaporator defrosting operation end condition is satisfied (step S113). The refrigerating evaporator defrosting operation end condition is satisfied when the refrigerating evaporator temperature _{TR_evp} is equal to or higher than the refrigerating evaporator defrosting operation end temperature _{TRD_off} (= 2 ° C.) ( _{TR_evp} ≧ _{TRD_off} ). When step S113 is established (Yes), the refrigerating fan 9a is stopped (step S114), and the "refrigerating evaporator defrosting operation" ends.

If step S113 is not satisfied (No), it is subsequently determined whether the refrigerating operation end condition is satisfied (step S115). In the refrigerator of this embodiment, when the vegetable compartment damper 19 is closed and the freezing chamber temperature _TF is the freezing operation end temperature _{TF_off} (= -22.5 ° C.) or less ( _TF ≧ _{TF_off} ), step S115. Is established. If step S115 is not satisfied (No), the process returns to the determination in step S110.

If step S115 is satisfied, it is next determined whether the refrigerating operation start condition is satisfied (step S116). In the refrigerator of this embodiment, in the refrigerator of this embodiment, the refrigerating room temperature TR detected by the refrigerating room temperature sensor 41 is _{equal to or higher than the refrigerating operation start temperature TR_on (} = 5.5 ° C.) ( _{TR ≧ TR_on )} . In the case of, step S116 is established.

If step S116 is established (if not established (No) will be described later), the drive rotation speed of the compressor 24 is maintained, the three-way valve 52 is set to state 3 (fully closed mode), and the inside of the refrigerating evaporator 14b is set. A refrigerant recovery operation for recovering the refrigerant to the heat dissipation means side is performed (step S117). At this time, the refrigerating fan 9b continues to be driven and cools the freezing chamber 7 even during the refrigerant recovery operation.

If step S104 is not established (No), it is determined whether to subsequently perform the refrigerating evaporator defrosting operation (step S201). In the refrigerator of this embodiment, if the setting of the chilled room 35 provided in the lower part of the refrigerating chamber 2 is "temperature level 1" for maintaining the temperature at about 0 to 3 ° C. in the refrigerating temperature range, step S106 is performed. If "Yes" and "Temperature level 2" that maintains the temperature in the freezing temperature range of about -3 to 0 ° C. is selected, step S106 is rejected (No) (the same determination as in step S106). ). When step S201 is established (Yes), the refrigerating fan 9a is set to a speed of 1 (900min ^-1 ), the refrigerating evaporator defrosting operation is started (step S202), and when step S106 is rejected (No). The refrigerating fan 9a is stopped (step S203), the three-way valve 52 is set to state 3 (fully closed mode), the compressor 24 is stopped, and the refrigerating fan 9b is stopped (step S118). Further, even when step S116 is not established (No), the compressor 24 is stopped and the refrigerating fan 9b is stopped (step S118) with the three-way valve 52 in state 3 (fully closed mode).

Subsequently, it is determined whether or not the inside of the refrigerator has a high load (step S119). In the refrigerator of this embodiment, the freezing room temperature T _F detected by the freezing room temperature sensor 42 is a high load determination temperature T _{F_high} (= -10 ° C.) or higher ( _TF ≧ T _{F_high} ), or the refrigerating room temperature sensor 41. Step S119 is established when the refrigerating room temperature TR detected by is _{equal to or higher than the high load determination temperature TR_high (} = 10 ° C.) ( _{TR ≧ TR_high )} (the same determination as in steps S102 and 110). The control when step S119 is established will be described later.
If step S119 is not satisfied (No), then it is determined whether the refrigerating evaporator defrosting operation end condition is satisfied (step S120). The refrigerating evaporator defrosting operation end condition is satisfied when the refrigerating evaporator temperature _{TR_evp} is equal to or higher than the refrigerating evaporator defrosting operation end temperature _{TRD_off} (= 2 ° C.) ( _{TR_evp} ≧ _{TRD_off} ) (step). Judgment similar to S113). When step S120 is established (Yes), the refrigerating fan 9a is stopped (step S121), and "end of refrigerating evaporator defrosting operation" ends.

If step S120 is not satisfied (No), it is subsequently determined whether the frozen vegetable operation start condition is satisfied (step S122). In the refrigerator of this embodiment, step S122 is established when the freezing room temperature _TF detected by the freezing room temperature sensor 42 is equal to or higher than the frozen vegetable operation start temperature _{TF_on} (= -18 ° C.) ( _TF ≧ _{TF_on} ). (Determination similar to step S104). If step S122 is established (Yes), then it is determined whether or not the refrigerant recovery operation needs to be performed (step S123). In the refrigerator of this embodiment, step S123 is established when the operation immediately before the compressor 24 is stopped by step S118 is the refrigerating operation. When step S123 is established (Yes), the three-way valve 52 is set to state 3 (fully closed mode), the compressor 24 is driven at the rotation speed in the immediately preceding refrigerating operation, and the refrigerant in the refrigerating evaporator 14a is dissipated. The refrigerant recovery operation for recovering to the side is carried out (step S124), and the frozen vegetable operation is started (step S109). If step S123 is not established (No), the frozen vegetable operation is started without performing the refrigerant recovery operation (step S109).

If step S122 is not satisfied (No), it is subsequently determined whether the refrigerating operation start condition is satisfied (step S125). In the refrigerator of this embodiment, step S116 is established when the refrigerating room temperature TR detected by the refrigerating room temperature sensor 41 is _{equal to or higher than the refrigerating operation start temperature TR_on (} = 5.5 ° C.) ( _{TR ≧ TR_on )} . (Determination similar to step S116).

If step S125 is established, it is next determined whether or not the refrigerant recovery operation is necessary (step S126). In the refrigerator of this embodiment, step S126 is established when the operation immediately before the compressor 24 is stopped by step S118 is the freezing operation. When step S126 is established (Yes), the three-way valve 52 is set to the state 3 (fully closed mode), the compressor 24 is driven at the rotation speed in the immediately preceding refrigerating operation, and the refrigerant in the refrigerating evaporator 14b is dissipated. The refrigerant recovery operation for recovery is performed on the side (step S127), and the refrigeration operation is started (step S101). If step S126 is not established (No), the refrigerating operation is started without performing the refrigerant recovery operation (step S101).

In the above description, the refrigerating operation start temperature _{TR_on} (= 5.5 ° C), the refrigerating operation end temperature _{TR_off} (= 2.5 ° C) _{, the} frozen vegetable operation start temperature _{TF_on} (= -18 ° C), and the refrigerating operation The end temperature _{TF_off} (= -22.5 ° C.) is an example when the maintenance temperature level of the refrigerator compartment 2 is set to "medium" and the maintenance temperature level of the freezer compartment 7 is set to "medium". It varies according to the maintenance temperature level.

Next, control when the inside of the refrigerator 1 has a high load will be described with reference to FIG. The control shown in FIG. 8 shifts to the case where it is determined in steps S102, S110, and S119 of FIG. 7 that the inside of the refrigerator 1 has a high load (the determination in each step is Yes). When it is determined that the inside of the refrigerator has a high load, it is subsequently determined whether the refrigerating chamber 2 has a high load (step S301) or the freezing chamber 7 has a high load (step S302). If the refrigerating chamber 2 has a high load and the freezing chamber 7 does not have a high load, step S301 becomes No, and then the necessity of the refrigerant recovery operation is determined (step S501).

In the refrigerator of this embodiment, step S501 is established when the operation at the time when any of steps S102, S110, and S119 of FIG. 7 is established is the refrigerating operation. When step S501 is established (Yes), the three-way valve 52 is set to the state 3 (fully closed mode), the compressor 24 is driven at the rotation speed in the immediately preceding refrigerating operation, and the refrigerant in the refrigerating evaporator 14a is dissipated. A refrigerant recovery operation for recovering to the side is performed (step S502), and then "high load mode frozen vegetable operation" is selected (step S503). If step S501 is not established (No), "high load mode frozen vegetables / freezing operation" is selected without performing the refrigerant recovery operation (step S503). In the refrigerator of this embodiment, when "high load mode frozen vegetables / frozen operation" is selected, the compressor 24 has a speed of 4 (3600 min ^-1 ) as the rotation speed when the frozen vegetables operation or the freezing operation is performed. , The freezing fan 9b is set to a speed of 2 (2000min ^-1 ). The rotation speed of the compressor 24 and the refrigerating fan 9a when the refrigerating operation and the refrigerating evaporator defrosting operation are performed is selected to be the same as the rotation speed of the normal operation mode.

If the freezing chamber 7 has a high load (Yes in step S301) and the refrigerating chamber 2 does not have a high load, step S302 becomes No, and then the necessity of the refrigerant recovery operation is determined (step S401).

In the refrigerator of this embodiment, step S401 is established when the operation at the time when any of steps S102, S110, and S119 of FIG. 7 is established is frozen vegetable operation or frozen operation. When step S401 is established (Yes), the three-way valve 52 is set to the state 3 (fully closed mode), the compressor 24 is driven at the rotation speed in the immediately preceding frozen vegetable operation or the freezing operation, and the inside of the refrigerating evaporator 14b is driven. A refrigerant recovery operation for recovering the refrigerant to the heat dissipation means side is performed (step S402), and then "high load mode refrigeration operation" is selected (step S403). If step S401 is not established (No), "high load mode refrigeration operation" is selected without performing the refrigerant recovery operation (step S403). In the refrigerator of this embodiment, when "high load mode refrigeration operation" is selected, the rotation speed of the compressor 24 is set to speed 3 (2500 min ^-1 ) and the rotation speed of the refrigeration fan 9a is set to speed 3 (2000 min ^-1 ). To. The rotation speed of the compressor 24, the refrigerating fan 9a, and the refrigerating fan 9b when the frozen vegetable operation, the freezing operation, and the refrigerating evaporator defrosting operation are performed is selected to be the same as the normal operation mode. ..

When both the freezing chamber 7 and the refrigerating chamber 2 have a high load (Yes in step S301 and step S302), it is next determined whether or not the refrigerant recovery operation is necessary (step S303). In the refrigerator of this embodiment, step S303 is established when the operation at the time when any of steps S102, S110, and S119 of FIG. 7 is established is the refrigerating operation. When step S303 is established (Yes), the three-way valve 52 is set to the state 3 (fully closed mode), the compressor 24 is driven at the rotation speed in the immediately preceding refrigerating operation, and the refrigerant in the refrigerating evaporator 14a is dissipated. A refrigerant recovery operation for recovery is performed on the side (step S304), and then the "overload mode" is selected (step S305). In the refrigerator of this embodiment, when the "overload mode" is selected, the compressor 24 has a speed of 3 (2500 min ^-1 ) and the refrigerating fan 9a has a speed of 3 (2500 min -1) as the rotation speed when the refrigerating operation is performed. 2000min ^-1 ), the rotation speed when the frozen vegetable operation or the freezing operation is performed is set to the speed 4 (3600min ^-1 ) for the compressor 24 and the speed 2 (2000min ^-1 ) for the refrigerating fan 9b. The rotation speed of the refrigerating fan 9a when the refrigerating evaporator defrosting operation is performed is selected to be the same as the rotation speed of the normal operation mode.

When "overload mode" is selected in step S305, the three-way valve 52 is set to state 2 (refrigerating mode), the compressor 24 is set to speed 4 (3600min ^-1 ), and the refrigerating fan 9b is set to speed 2 (2000min ^-1 ). The vegetable compartment damper 19 is opened and the frozen vegetable operation is started (step S306), and then the refrigerating fan 9a is driven at a speed of 1 (900min ^-1 ) to defrost the refrigerating evaporator. Will be implemented.

Next, it is determined whether or not the vegetable room cooling end condition is satisfied (step S308). In the refrigerator of this embodiment, step S307 is established when the vegetable room temperature _{TV detected by the vegetable room temperature sensor 43 is equal to or less than the vegetable room cooling end temperature TV_off (} = 6 ° C.) ( _{TV ≤ TV_off )} . .. When step S308 is established (Yes), the vegetable compartment damper 19 is closed, the frozen vegetable operation ends, and the freezing operation shifts to cooling the freezing chamber 7 (step S309).

If step S308 is not satisfied (No), it is subsequently determined whether or not the refrigerating evaporator defrosting operation end condition is satisfied (step S310). The refrigerating evaporator defrosting operation end condition is satisfied when the refrigerating evaporator temperature _{TR_evp} is equal to or higher than the refrigerating evaporator defrosting operation end temperature _{TRD_off} (= 2 ° C.) ( _{TR_evp} ≧ _{TRD_off} ). When step S310 is established (Yes), the refrigerating fan 9a is stopped, and the refrigerating evaporator defrosting operation is completed (step S311).

If step S310 is not satisfied (No), it is subsequently determined whether the frozen vegetable operation or the freezing operation end condition is satisfied (step S312). In the refrigerator of this embodiment, when the vegetable compartment damper 19 is closed and the freezing chamber temperature _TF is the freezing operation end temperature _{TF_off} (= -22.5 ° C.) or less ( _TF ≧ _{TF_off} ), or Step S312 is established when the frozen vegetable operation or the duration of the frozen operation reaches a predetermined value (42.5 minutes). If step S312 is not established (No), the process returns to the determination in step S308.

When step S312 is established (Yes), the three-way valve 52 is set to the state 3 (fully closed mode), and the refrigerant recovery operation for recovering the refrigerant in the refrigerating evaporator 14b to the heat dissipation means side is performed (step S313). At this time, the freezing fan 9b continues to be driven.

Subsequently, it is determined whether or not to shift to the normal operation mode (step S314). In the refrigerator of this embodiment, the refrigerating room temperature TR detected by the refrigerating room temperature sensor 41 is less than or _equal to the refrigerating operation start temperature _{TR_on} (= 5.5 ° C.) ( _TR ≤ T _{_on} ), and the refrigerating room temperature sensor 42 detects it. Step S314 is established (Yes) when the freezer temperature _TF is simultaneously satisfied with the frozen vegetable operation start temperature _{TF_on} (= -18 ° C) or less ( _{TR ≤ T F_on )} , and the normal operation mode is set. Return (step S101 in FIG. 7)
If step S314 is not established (No), the refrigerating operation is subsequently performed (step S315). In the refrigerating operation, the three-way valve 52 is set to state 1 (refrigerating mode), the compressor 24 is driven at a speed of 3 (2500 min ^-1 ), the refrigerating fan 9a is driven at a speed of 3 (2000 min ^-1 ), and the refrigerating fan 9b. Is stopped, and the vegetable room damper 19 is closed to start.

Next, it is determined whether the freezing chamber 7 has a high load (step S316). In the refrigerator of this embodiment, step S316 is established when the freezing room temperature _TF detected by the freezing room temperature sensor 42 is the high load determination temperature _{TF_high} (= -10 ° C.) or higher ( _TF ≧ _{TF_high} ). (Yes). When step S316 is established (Yes), the refrigerant recovery operation is performed (step S304), and the mode shifts to the overload mode (step S305). The determination in step S316 is skipped until a predetermined time (5 minutes) has elapsed from the start of the refrigerating operation.

If step S316 is not satisfied (No), the process proceeds to determination of whether the refrigerating operation end condition is satisfied (step S317). In the refrigerator of this embodiment, when the refrigerating chamber temperature _{TR is the refrigerating operation end temperature TR_off (} = 2.5 ° C.) or less ( _{TR ≤ TR_off )} , or in the overload mode, the duration of the refrigerating operation is predetermined. When the value (20.5 minutes) is reached, step S317 is established. If step S317 is not established (No), the determination in step S316 is returned again, and if step S317 is established (Yes), the three-way valve 52 is set to state 3 (fully closed mode) and the refrigerating evaporator 14a is set. A refrigerant recovery operation for recovering the refrigerant to the heat dissipation means side is performed (step S318). At this time, the refrigerating fan 9a continues to be driven.

Subsequently, it is determined whether or not to shift to the normal operation mode (step S319). In the refrigerator of this embodiment, the refrigerating room temperature TR detected by the refrigerating room temperature sensor 41 is less than or _{equal to the refrigerating operation start temperature TR_on (} = 5.5 ° C.) ( _{TR ≤ TR_on )} , and the refrigerating room temperature sensor 42 detects it. Step S318 is established (Yes) when the freezer temperature _TF is simultaneously satisfied with the frozen vegetable operation start temperature _{TF_on} (= -18 ° C) or less ( _{TR ≤ T F_on )} , and the normal operation mode is set. Return (step S109 in FIG. 7).

If "high load mode refrigerated operation" is selected in step S403, the process proceeds to step S315 to start the refrigerated operation, and if "high load mode frozen vegetables / frozen operation" is selected in step S503, the process proceeds to step S315 and the refrigerated operation is started. , The operation of frozen vegetables is started in step S306, and thereafter, control is performed according to the above-mentioned control flow.

In the refrigerator of this embodiment, the refrigerant recovery operation in steps S105 and S301 is performed when the compressor 24 is driven at a speed of 1 (800 min ^-1 ) and the refrigerating fan 9a is driven at a speed of 2 (1500 min ^-1 ). For 2 minutes, the compressor 24 is driven at a speed of 3 (2500 min ^-1 ) and the refrigerating fan 9a is driven at a speed of 3 (2000 min ^-1 ) for 1.5 minutes. Further, the refrigerant recovery operation in steps S112 and S302 is compressed for 2.5 minutes when the compressor 24 is driven at a speed of 2 (1400 min ^-1 ) and the refrigerating fan 9b is driven at a speed of 1 (1200 min ^-1 ). If the machine 24 is driven at a speed of 4 (1400 min ^-1 ) and the refrigerating fan 9b is driven at a speed of 2 (2000 min ^-1 ), this is carried out for 1.5 minutes.

The circulating air volume of the refrigerating chamber 2 at the rotation speed (speed 2 = 1500 min ^-1 ) of the refrigerating fan 9a during the refrigerating operation in the normal operation mode is 0.52 m ³ / min. Further, the circulating air volume of the refrigerating chamber 2 at the rotation speed (speed 1 = 900min ^-1 ) of the refrigerating fan 9a during the refrigerating evaporator defrosting operation is 0.31 m ³ / min.

The circulating air volume of the freezing chamber 7 at the rotation speed of the freezing fan 9b in the normal operation mode (speed 1 = 1200 min ^-1 ) is 0.55 m ³ / min when the vegetable compartment damper 19 is open (during frozen vegetable operation). When the vegetable compartment damper 19 is closed (during freezing operation), it is 0.6 m ³ / min, and when the vegetable compartment damper 19 is open (during frozen vegetable operation), the circulating air volume of the vegetable chamber 6 is 0. It is 07m ³ / min.

The circulating air volume of the refrigerating chamber 2 at the rotation speed (speed 3 = 2000 min ^-1 ) of the refrigerating fan 9a during the refrigerating operation in the high load mode or the overload mode is 0.52 m ³ / min. In addition, the circulating air volume of the freezing chamber 7 at the rotation speed of the freezing fan 9b in the high load mode (speed 2 = 2000 min ^-1 ) is 0.92 m ³ when the vegetable compartment damper 19 is open (during frozen vegetable operation). / Min, 1.0 m ³ / min when the vegetable compartment damper 19 is closed (during frozen vegetable operation), and the circulating air volume of the vegetable compartment 6 when the vegetable compartment damper 19 is open (during frozen vegetable operation). It is 0.12 m ³ / min.

FIG. 9 is a time chart showing a state in which the refrigerator according to this embodiment is installed in an environment of 32 ° C. and a relative humidity of 70%, and stable cooling operation is performed in the normal operation mode. The maintenance temperature level of the refrigerator compartment 2 is set to "medium", the maintenance temperature level of the freezer compartment 7 is set to "medium", and the maintenance temperature level of the chilled chamber 35 is set to "temperature level 1".

The elapsed time t ₀ is the elapsed time when the refrigerating operation for cooling the refrigerating chamber 2 is started (step S101 in FIG. 7). In the refrigerating operation in the normal operation mode, the three-way valve 52 is controlled to the state 1 (refrigerating mode), the compressor 24 is driven at a speed of 1 (800min ^-1 ), and the refrigerant is supplied to the refrigerating evaporator 14a. , The temperature of the refrigerating evaporator 14a has dropped. In this state, the refrigerating fan 9a is driven at a speed of 2 (1500min ^-1 ), so that the air that has passed through the refrigerating evaporator 14a and has become low temperature flows from the refrigerating chamber discharge port 11a (see FIG. 2) to the refrigerating chamber. The temperature is lowered by blowing out into the refrigerator 2 and cooling the refrigerator compartment 2.

Here, the time average temperature of the refrigerating evaporator 14a during the refrigerating operation is −6 ° C., which is higher than the time average temperature of −24 ° C. of the refrigerating evaporator 14b during the refrigerating operation, which will be described later. Generally, the higher the evaporator temperature (evaporation temperature), the higher the coefficient of performance of the refrigeration cycle (the ratio of the amount of heat absorbed to the input of the compressor 24), and the higher the energy saving performance. In the freezer chamber 7, it is necessary to lower the temperature of the refrigerating evaporator 14b in order to maintain the freezing temperature, but since the refrigerating chamber 2 may be maintained at the refrigerating temperature, the temperature of the refrigerating evaporator 14a should be increased. The rotation speed of the refrigerating fan 9a and the compressor 24 is controlled to improve the energy saving performance. Since the refrigerating room temperature TR detected by the refrigerating room temperature sensor 41 at the elapsed time _{t1 drops to the refrigerating operation end temperature TR_off ,} the refrigerating operation is switched to the refrigerant recovery operation (steps S104 and S105 in FIG. 7). ). In the refrigerant recovery operation, the three-way valve 52 is controlled to state 3 (fully closed mode), the compressor 24 is driven at a speed of 1 (800 min ^-1 ), and the refrigerating fan 9a is driven at a speed of 2 (1500 min ^-1 ) for refrigeration. The refrigerant in the evaporator 14a is recovered for 2 minutes ( _ΔTA1 = 2min). As a result, it is possible to suppress a decrease in cooling efficiency due to a shortage of refrigerant in the next frozen vegetable operation and the freezing operation. At this time, by driving the refrigerating fan 9a, the residual refrigerant in the refrigerating evaporator 14a is utilized for cooling the refrigerating chamber 2, and the refrigerating evaporator is heated by the air in the refrigerating chamber 2. The pressure drop in 14a is alleviated. As a result, the increase in the specific volume of the suction refrigerant of the compressor 24 is suppressed, a large amount of refrigerant can be recovered in a relatively short time, and the cooling efficiency can be improved.

When the refrigerant recovery operation is completed (elapsed time t ₂ ), it is determined whether to carry out the refrigerating evaporator defrosting operation. Here, since the setting of the chilled room 35 is "temperature level 1", the refrigerating fan 9a is driven at a speed of 1 (900 min ^-1 ) to perform a refrigerating evaporator defrosting operation (steps S106 and S107 in FIG. 7). As a result, the temperature of the refrigerating evaporator 14a rises, and the temperature rise of the refrigerating chamber 2 is alleviated by the cooling effect of frost and the cold storage heat of the refrigerating evaporator 14a. Further, since the freezing room temperature _TF detected by the freezing room temperature sensor 42 at the elapsed _time t2 is equal to or higher than the frozen vegetable operation start temperature _{TF_on} , the frozen vegetable operation is started, the vegetable room 6 is cooled, and the vegetable room 6 is cooled. The temperature _TV is decreasing. In frozen vegetable operation, the three-way valve 52 is controlled to state 2 (freezing mode), the compressor 24 is driven at a speed of 2 (1400 min ^-1 ), refrigerant is supplied to the refrigerating evaporator 14b, and the refrigerating evaporator is operated. 14b becomes low temperature. In this state, the vegetable compartment damper 19 is opened, and the freezing fan 9b is driven at a speed of 1 (1200min ^-1 ), so that the freezing chamber 7 and the vegetables pass through the freezing evaporator 14b and become cold. The chamber 6 is cooled.

When the vegetable room temperature _{TV detected by the vegetable room temperature sensor 43 reaches the vegetable room cooling end temperature TV_off at} the elapsed time t ₃ , the vegetable room damper 19 is closed and the freezing operation is started (FIG. 7). Steps S111 and S112).

Subsequently, when the temperature T _Revp of the refrigerating evaporator 14a detected by the refrigerating evaporator temperature sensor 40a reaches the refrigerating evaporator defrosting operation end temperature _{TRD_off} at the elapsed time _t4 , the refrigerating fan 9a is stopped. Then, the refrigerating evaporator defrosting operation is completed (steps S113 and S114 in FIG. 7).

Since the freezing room temperature _TF detected by the freezing room temperature sensor 42 at the elapsed time _{t5 reaches the freezing operation end temperature TF_off and} the vegetable room damper 19 is closed, the freezing operation is finished. (Step S115 in FIG. 7). At this time, since the refrigerating room temperature T _R detected by the refrigerating room temperature sensor 41 has reached the refrigerating operation start temperature T _{R_on} or higher, the refrigerating operation start condition is satisfied (step S116 in FIG. 7), and the refrigerant recovery operation is performed. (Step S117 in FIG. 7). In the refrigerant recovery operation, the three-way valve 52 is controlled to the state 3 (fully closed mode), the compressor 24 is driven at a speed of 2 (1400 min ^-1 ), and the refrigerating fan 9b is driven at a speed of 1 (1200 min ^-1 ) to freeze. The refrigerant in the evaporator 14b is recovered for 1.5 minutes (Δt _B1 = 1.5 min). As a result, it is possible to suppress a decrease in cooling efficiency due to a shortage of refrigerant in the next refrigeration operation. At this time, by driving the freezing fan 9b, the residual refrigerant in the freezing evaporator 14b is utilized for cooling the freezing chamber 7, and the inside of the freezing evaporator 14b is heated by the air in the freezing chamber 7. Pressure drop is alleviated. As a result, the increase in the specific volume of the suction refrigerant of the compressor 24 is suppressed, a large amount of refrigerant can be recovered in a relatively short time, and the cooling efficiency can be improved.

The operations in which the freezing chamber 7 is cooled are the frozen vegetable operation (t2 to t3), the freezing operation (t3 to t5), and the refrigerant recovery operation (t5 to t6), and are for freezing while these operations are performed. The refrigerating fan 9b and the compressor 24 are controlled so that the time average temperature of the evaporator 14b is about −24 ° C. The time average value of the temperature of the discharged air in the refrigerating chamber during the refrigerating operation, the refrigerant recovery operation, and the refrigerating evaporator defrosting operation in which the refrigerating fan 9a is driven is -1.5 ° C. The temperature is higher than the arithmetic mean value (-8 ° C) of the freezing room maintenance temperature _{TF_keep} (-20 ° C) and the refrigerating room maintenance temperature _{TR_keep} (4 ° C).

The refrigerating operation is started again from the elapsed time t6 when the refrigerant recovery operation is completed (step S101 in FIG. ₇ ), and thereafter, the above-mentioned operation is periodically repeated. The temperature is maintained at -20 ° C and the vegetable compartment is maintained at about 7 ° C.

FIG. 10 is a time chart showing an operating state when the refrigerator according to this embodiment is installed in an environment of 32 ° C. and the load cooling test specified in JISC9801-3: 2015 is carried out. In a refrigerator, it is important not only that the cooling operation is performed stably without opening and closing the door, but also that the refrigerator is cooled well when a practical load such as food is applied. .. After fully considering how to use a general refrigerator, JISC9801-3: 2015 stipulates a "load cooling test" assuming a practical load (hereinafter referred to as "practical load"). As a practical load, water with the same temperature as the outside air temperature is used, 12 g per 1 L rated internal volume of the refrigerated temperature zone room (refrigerator room and vegetable room), and 4 g per 1 L rated internal volume of the refrigerating temperature zone room (freezer chamber). It is stipulated that the water from the refrigerator should be put into the refrigerator and freezer, respectively.

At the elapsed time t0 in which the refrigerating operation (see FIG. 9) is being performed in the stable cooling operation, the door 2a of the refrigerating room 2 is opened for 1 minute according to the procedure specified in JISC9801-3: 2015, and the refrigerating temperature zone room is used. As a practical load of (refrigerating room 2 and vegetable room 6), 5064 g of water at 32 ° C. (load for the rated internal volume of 422 L of the refrigerated temperature zone room (refrigerating room 2 and vegetable room 6)) is enclosed in a 500 mL PET bottle and refrigerated. It is installed at a predetermined position in the room 2. Subsequently, the door 5a of the freezing chamber 7 (lower freezing chamber 5) is opened for 1 minute, and 720 g of water at 32 ° C. (load for the rated internal volume of 180 L of the freezing temperature zone chamber (freezing chamber 7)) is applied to the freezing chamber 7 (load). It is installed at a predetermined position in the lower freezing room 5).

As a result, the refrigerating chamber temperature TR first _{rises and exceeds the refrigerating chamber high load determination temperature TR_high ,} so that the refrigerating chamber 2 is determined to have a high load (step S110 in FIG. 7). At this point, the refrigerating chamber temperature TR exceeds the refrigerating chamber high load determination temperature _{TR_high} and is determined to be a high load, but the freezing chamber temperature _{T F has} not reached the high load determination temperature T _{F_high} . Therefore, although step S301 in FIG. 8 holds (Yes), step S302 does not hold (No), so that the necessity of the refrigerant recovery operation is next determined (step S401 in FIG. 8). Since the operation mode when the determination in step S110 is made is the refrigerating operation, it is determined that the refrigerant recovery operation is necessary here (step 401 in FIG. 8 is Yes), the compressor 24 has a speed of 2 (1400min ^-1 ), and the refrigerating operation is performed. A refrigerant recovery operation is performed in which the refrigerant in the refrigerating evaporator 14b is recovered for 2.5 minutes (Δt _A2 = 2.5 min) while the fan 9b is driven at a speed of 1 (1200 min ^-1 ). (Step S402 in FIG. 8). At this time, by driving the freezing fan 9b, the freezing chamber 7 is cooled by the endothermic action of the residual refrigerant in the freezing evaporator 14b (freezing chamber cooling operation (F)).

The refrigerant recovery operation is completed at the elapsed time t ₀ ', and then the three-way valve 52 is controlled to the state 1 (refrigerating mode), the compressor 24 has a speed of 3 (2500min ^-1 ), and the refrigerating fan 9a has a speed of 3 (refrigerating mode). A high load mode refrigerating operation is performed in which the refrigerating fan 9b is driven at 2000 min ^-1 ) and is stopped (steps S403 and S315 in FIG. 8).

Due to the practical load applied to the freezing chamber 7 (lower freezing chamber 5), the freezing chamber temperature _TF rises and exceeds the high load determination temperature _{TF_high} , but it is shown in FIG. 8 until 5 minutes have passed after the transition to the refrigerating operation. Since step S316 is not established, the high load mode refrigerating operation is continued.

When 5 minutes, which is the minimum elapsed time after the refrigerating operation transition condition is satisfied, has elapsed at the elapsed time t ₁ , step S316 shown in FIG. 8 is established (Yes), and the refrigerant recovery operation (step S304 in FIG. 8) is performed. , The overload mode is entered at the elapsed time t1 (step S305 in FIG. 8). In the refrigerant recovery operation at this time, the three-way valve 52 is controlled to the state 3 (fully closed mode), the compressor 24 is driven at a speed of 3 (2500min ^-1 ), and the refrigerating fan 9a is driven at a speed of 3 (2000min ^-1 ). Then, the refrigerant in the refrigerating evaporator 14a is recovered for 1.5 minutes (Δt _B2 = 1.5min). This refrigerant recovery operation is completed in the elapsed time t ₁ '. During the refrigerant recovery operation, the refrigerating fan 9a is driven, and the refrigerating chamber 2 is cooled by the endothermic action of the residual refrigerant in the refrigerating evaporator 14a.

From this elapsed time t _0'to the elapsed time t ₁ ', the refrigerating chamber is in an operating state (refrigerating chamber cooling operation (R)) in which the refrigerating chamber is cooled.

From the elapsed time t ₁ , the overload mode is set, and the frozen vegetable operation for cooling the freezing chamber 7 is started (step S306 in FIG. 8). In the operation of frozen vegetables in the overload mode, the three-way valve is controlled to state 2 (freezing mode), the compressor 24 is driven at a speed of 4 (3600min ^-1 ), and the freezing fan 9b is driven at a speed of 2 (2000min ^-1 ). This is done with the vegetable compartment damper 19 open. This operation cools the freezing chamber 7 and the vegetable compartment 6. At this time, the refrigerating fan 9a is driven at a speed of 1 (900min ^-1 ), so that the refrigerating evaporator defrosting operation is performed (step S307 in FIG. 8). When the temperature T _Revp of the refrigerating evaporator 14a detected by the refrigerating evaporator temperature sensor 40a reaches the refrigerating evaporator defrosting operation end temperature _{TRD_off} at the elapsed time t ₂ , the refrigerating fan 9a is stopped. , The refrigerating evaporator defrosting operation has been completed (steps S310 and S311 in FIG. 8).

When the vegetable room temperature _{TV detected by the vegetable room temperature sensor 43 reaches the vegetable room cooling end temperature T V_off or} less ( _{TV ≤ T V_off )} at the elapsed time t ₃ , the vegetable room damper 19 is closed and the freezing operation is performed. (Steps S308 and S309 in FIG. 8).

At the elapsed time t4, the elapsed time from the start of the frozen vegetable operation in the overload mode reached a predetermined value ₍ 42.5 min), so that the frozen vegetable / frozen operation end condition was satisfied (step S312 in FIG. 8), and the frozen operation was performed. Has been completed, and the operation is shifting to the refrigerant recovery operation. In the refrigerant recovery operation at this time, the three-way valve 52 is controlled to the state 3 (fully closed mode), the compressor 24 is driven at a speed of 4 (3600 min ^-1 ), and the refrigerating fan 9b is driven at a speed of 2 (2000 min ^-1 ). Then, the refrigerant in the refrigerating evaporator 14b is recovered for 1.5 minutes (Δt _C2 = 1.5 min). This refrigerant recovery operation is completed in the elapsed time t ₄ '. During the refrigerant recovery operation, the refrigerating fan 9b is driven, and the freezing chamber 7 is cooled by the endothermic action of the residual refrigerant in the refrigerating evaporator 14b. From the above, from the above, the elapsed time t _1'to t _4'is the operation in which the freezing chamber 7 is cooled (freezing chamber cooling operation (F)).

Subsequently, the transition to the normal operation mode is determined (step S312 in FIG. 8), but in the elapsed time t ₄ ', both the refrigerating room temperature _{TR and the freezing room temperature T F are the refrigerating operation start temperature TR_on and frozen} vegetables. Since the operation start temperature is higher than _{TF_on} , the temperature is not satisfied, and the operation shifts to the refrigerating operation in the overload mode (step S315 in FIG. 8). As a result, the three-way valve 52 is controlled to state 1 (refrigerating mode), the compressor 24 is driven at a speed of 3 (2500min ^-1 ), the refrigerating fan 9a is driven at a speed of 3 (2000min ^-1 ), and the refrigerating fan 9b is driven. The refrigerating operation in the overload mode in the stopped state is performed (steps S315 and S315 in FIG. 8).

When the duration of the refrigerating operation in the overload mode reaches a predetermined value ₍ 20.5 min) at the elapsed time t5, the refrigerating operation end condition is satisfied (step S317 in FIG. 8), and the operation shifts to the refrigerant recovery operation. (Step S318 in FIG. 8). In the refrigerant recovery operation at this time, the three-way valve 52 is controlled to the state 3 (fully closed mode), the compressor 24 is driven at a speed of 3 (2500 min ^-1 ), and the refrigerating fan 9a is driven at a speed of 3 (2000 min ^-1 ). Then, the refrigerant in the refrigerating evaporator 14a is recovered for 1.5 minutes. This refrigerant recovery operation is completed in the elapsed time t ₅ '(the same control as the refrigerant recovery operation performed in the elapsed time t ₁ to t ₁ '). From the above, the elapsed time t _4'to t _5'is an operation in which the refrigerating chamber 2 is cooled (refrigerating chamber cooling operation (R)).

After that, the refrigerating room 2, the freezing room 7, and the vegetable room 6 are cooled by the same control as the elapsed time t _{1'to t 5 '} . Specifically, the elapsed time t ₅ to t ₈ and t ₉ to t ₁₂ and t ₁₃ to t ₁₇ are the freezing room cooling operation, and the elapsed time t ₈ to t ₉ and t ₁₂ to t ₁₃ and t ₁₇ to t ₁₉ are. The refrigerating room will be cooled. Further, a refrigerating evaporator defrosting operation is carried out at t ₅ to t ₆ , t ₉ to t ₁₀ , and t ₁₃ to t ₁₄ .

Whether or not the practical load is sufficiently cooled depends on whether or not the refrigerating room temperature TR is cooled to the refrigerating room maintenance temperature TR _keep + 1 ° C or lower and the freezing room temperature T _F is cooled to the freezing room maintenance temperature T _{F keep} + 1 ° C or less. It can be judged. The refrigerating room maintenance temperature TR _keep + 1 ° C. or lower and the freezing room maintenance temperature _{TF keep} + 1 ° C. or lower may not be satisfied at the same time. In the present specification, the period from the time when the load is applied to the refrigerating chamber 2 to the state where the practical load applied to the refrigerating chamber 2 and the freezing chamber 7 can be regarded as sufficiently cooled is referred to as a load cooling section. In the refrigerator of this embodiment, the freezing room temperature _TF reaches the freezing room maintenance temperature _{TF_keep} + 1 ° C. at _t16 shown in FIG. 10, and the refrigerating room temperature _TR reaches the refrigerating room keeping temperature _{TR_keep} + 1 ° C. at _t18 . Since it has reached, the load cooling section is from t ₀ when the practical load is put into the refrigerating chamber 2 to t ₁₈ where it can be considered that the practical load of the refrigerating chamber 2 and the freezing chamber 7 is sufficiently cooled.

Here, in the refrigerator of the present embodiment, the cooling state of the practical load applied to the refrigerating chamber 2 and the refrigerating chamber 7 is detected by the refrigerating chamber temperature _TR detected by the refrigerating chamber temperature sensor 41 and the refrigerating chamber temperature sensor 42. Although it is possible to discriminate by the freezer temperature TF, the refrigerating room 2 and the freezing room 7 are represented by the method specified in JISC9801-1: 2015 in order to more reliably determine the cooling state of the practical load. The temperature may be measured and the cooling state of the practical load may be determined based on the temperature.
At the elapsed time t ₁₉ , it is determined whether or not to shift to the normal operation mode (step S319 in FIG. 8), the refrigerating room temperature TR is _{equal to or less than the refrigerating operation start temperature TR_on ( TR ≤ TR_on )} , and the freezing room is freezing. Since the temperature _TF simultaneously satisfies the frozen vegetable operation start temperature _{TF_on} or less (TR ≤ _{TF_on} ), the overload mode ends (Yes in step _S319 in FIG. 8), and the normal operation mode is used after _t19 . Cooling is taking place.

In this way, by applying a practical load to the refrigerating chamber 2 and the freezing chamber 7 at t ₀ , both the refrigerating chamber 2 and the freezing chamber 7 are in a high load state, so that the overload mode is set and the refrigerating chamber 2 is cooled. The operation to be performed (refrigerator room cooling operation) and the operation to cool the freezer room 7 ₍ refrigerator room cooling operation) are alternately performed, and the practical load is sufficiently cooled at t18, and the mode returns to the normal mode.

By the time the practical load is sufficiently cooled at t ₁₇₁₈ , the freezer temperature _TF is TF ₁ (= -7 ° C) at t ₁ , TF ₂ (= -11 ° C) at t ₅ ', and T at t ₉ . _{At F3} (= -14 ° C) and t13, the maximum value of T _{F4 (} = -16.5 ° C) is taken, but each maximum value gradually decreases ( _{TF1> T F2 >} T _F3 > T _F4 ). ..

Further, in the operation of the load cooling section (t ₀ to t ₁₈ ), the cooling room cooling operation (t _0'to t ₁ ', t _{4'to t 5 '} , t ₈ to t ₉ , where the refrigerating room 2 is cooled, The time average temperature T _{Revp_ave} of the refrigerating evaporator 14a in t ₁₂ to t ₁₃ and t ₁₇ to t ₁₈ ) is -6.0 ° C., and the freezer room 7 is cooled by the freezer room cooling operation (t ₀ to t ₀ ',. The time average temperature T _{Fevp_ave} of the refrigerating evaporator 14b in t _{1'to t 4', t 5'to t 8, t 9 to t 12, t 13 to t 17 ) is -23.0 °} C, and T _{Revp_ave.} > T _{Fevp_ave} .

Further, the time ratio (t _0'to t ₁₇ in the operation of t ₀ to t 17) during the operation from the time when the load is applied until the normal operation mode is restarted (t ₀ to t ₁₇ ) is the refrigerating room cooling operation. ₁ ', t _{4'to t 5 '} , t ₈ to t ₉ , t ₁₂ to t ₁₃ , t ₁₆ to t ₁₇ (time ratio) _RR = 34%, freezing room 7 is cooled Freezing room Vegetable room cooling Time ratio for operation or refrigerating room cooling operation (t ₀ to t ₀ ', t _{1'to t 4 '} , t _5'to t ₈ , t ₉ to t ₁₂ , t ₁₃ ~ in the operation of t ₀ to t ₁₇ (Time ratio of t ₁₆ ) _RF = 66%, and the ratio of the two is RF / _RR = _1.94 . On the other hand, the outside air temperature T _out (= 32 ° C.), the heat transfer area A _Revp (= 0.993 m ² ) on the air side of the refrigerating evaporator 14a, and the time average temperature of the refrigerating evaporator 14a during the cooling chamber cooling operation are T. _{Revp_ave} (= -6.0 ° C), refrigerating room maintenance temperature _{TR_keep} (= 4.0 ° C), air side heat transfer area A _Fevp (= 1.146m ² ) of refrigerating evaporator 14b, refrigerating evaporator The time average temperature during the freezing room cooling operation of 14b is T _{Fevp_ave} (= -23.0 ° C, the freezing room maintenance temperature is T _{F_keep} (= -20 ° C), and the rated contents of the refrigerating temperature zone room (refrigerating room and vegetable room) Product _VR (= 422L), freezer room rated internal volume V _F (= 180L), specific heat of water C _W (= 4.186kJ / kg ℃), specific heat of ice C _i (= 2.05kJ / kg ℃) ), As the coagulation latent heat L _W (= 333.6 kJ / kg) of water, {A _Revp × ( _{TR_keep} -T _{Revp_ave} )} / {A _Fevp × ( _{TF_keep} -T _{Fevp_ave} )} × {4 × _VF × (C _W x T _out -C _i x T _{F_keep} + L _W )} / [12 x _VR x {C _W x (T _{out -TR_keep} )}] is 1.78, which is R _F / _RR ( = 1.94) is higher. By controlling in this way, it is possible to achieve both a large-capacity freezer compartment and practical cooling performance (details will be described later).

The configuration and control method of the refrigerator of this embodiment have been described above. Next, the effects of the refrigerator of this embodiment will be described.

The refrigerator of this embodiment includes a refrigerating room 2 (first refrigerating temperature zone room), a vegetable room 6 (second refrigerating temperature zone room), and a freezing room 7, and a refrigerating evaporator 14a is provided on the back of the refrigerating room 2. (First evaporator) and refrigerating blower 9a (first blower), refrigerating evaporator 14b (second evaporator) and refrigerating fan 9b (second blower) are provided on the back of the freezer chamber 7, and the first The refrigerating air passage 111 (first air passage) that circulates the cooling air that exchanged heat with the refrigerating evaporator 14a by driving the blower to the refrigerating chamber 2 and the refrigerating evaporator 14b by driving the refrigerating fan 9b exchanged heat. An air flow blocking means (air flow blocking means) provided with a frozen vegetable air passage 112 (second air passage) for circulating cooling air to the freezing chamber 7 and the vegetable chamber 6 and blocking the air flow between the first air passage and the second air passage. It is provided with a heat insulating partition wall 28). As a result, the vegetable compartment and the refrigerator compartment can be cooled independently. For example, if food with a high temperature is stored in the vegetable compartment, or if food or the like is sandwiched between them, a gap is created between the vegetable compartment door and the heat insulating box. Even if the load on the vegetable compartment becomes large due to such reasons, it is not necessary to cool the refrigerator compartment together with the vegetable compartment, and it is possible to suppress excessive cooling of the refrigerator compartment, so that the cooling efficiency of the refrigerator compartment is reduced. It is possible to prevent. Further, unlike the configuration in which the vegetable compartment is indirectly cooled by the cold air of the freezing chamber through a partition wall as in Patent Document 1, the air exchanged with the freezing evaporator can be blown to the vegetable compartment for cooling. It is also possible to prevent a decrease in the cooling efficiency of the freezing chamber due to keeping the freezing chamber at an excessively low temperature. That is, since the load of a part of the storage chamber is cooled, the problem that the cooling efficiency of the refrigerator as a whole does not decrease is unlikely to occur, that is, the refrigerator has a high cooling efficiency of the refrigerator as a whole.

The refrigerator of this embodiment is the refrigerating room 2 (first refrigerating room) having the largest rated internal volume among the refrigerating room 2 (first refrigerating temperature zone room), the freezing room 7, and the vegetable room 6 (second refrigerating temperature zone room). The refrigerating air passage 111 (first air passage) that distributes the cooling air that has exchanged heat with the refrigerating evaporator 14a to the refrigerating chamber 2 and the cooling air that has exchanged heat with the refrigerating evaporator 14b in the refrigerating chamber 7). And an air flow blocking means (insulation partition wall 28) that is provided with a frozen vegetable air passage 112 (second air passage) to be distributed to the vegetable compartment 6 and blocks the air flow between the refrigerated air passage 111 and the frozen vegetable air passage 112. Is equipped with. In general, the larger the rated internal volume, the more food can be stored by the user, so the cooling load is often large in a storage room with a large rated internal volume. Therefore, of the refrigerating room 2 (first refrigerating temperature zone room), the freezing room 7, and the vegetable room 6 (second refrigerating temperature zone room), the refrigerating air passage for flowing cooling air to the refrigerating room 2 having the largest rated internal volume. By providing an air flow blocking means (insulation partition wall 28) so that air does not flow between the 111 and the frozen vegetable air passage 112, the other freezer chambers are affected by the load of the storage chamber having the maximum rated internal volume. It is possible to prevent the situation where foods in the vegetable room and the food in the vegetable room are heated, and the refrigerator has high cooling efficiency.

The refrigerator of this embodiment is located at the lower stage of the refrigerating air passage 111 (first air passage) for circulating cooling air to the refrigerating room 2 (first refrigerating temperature zone room) which is the uppermost storage room and the refrigerating room 2. A frozen vegetable air passage 112 (second air passage) for circulating cooling air is provided in the freezer chamber 7 and the vegetable chamber 6 to block the air flow between the refrigerated air passage 111 and the frozen vegetable air passage 112. The means (insulation partition wall 28) is provided. Generally, in an environment where a refrigerator is installed (for example, a kitchen), if the air is not actively agitated by an air conditioner or the like, a temperature distribution (temperature stratification) in the vertical direction is formed, and the air is formed upward. The temperature tends to be high. Therefore, in the uppermost storage room, air with a higher temperature tends to flow in when the door is opened and closed, and the load tends to increase. Therefore, in the refrigerator of this embodiment, the refrigerating air passage 111 for circulating the cooling air to the refrigerating chamber 2 (first refrigerating temperature zone chamber) which is the uppermost storage chamber, the refrigerating chamber 7 which is the lower storage chamber, and the refrigerating chamber 7 are used. By providing an air flow blocking means (insulation partition wall 28) so that air does not flow between the frozen vegetable air passages 112 that allow cooling air to flow in the vegetable room 6, the load on the uppermost storage room causes the other It is possible to prevent the situation where foods in the storage room (freezer room and vegetable room) are heated, and the refrigerator has high cooling efficiency.

In the case of a refrigerator such as the refrigerator of this embodiment, in which the refrigerating room (freezing temperature zone room), the freezing room (freezing temperature zone room), and the vegetable room (refrigerating temperature zone room) are arranged in this order from the top, the refrigerating room is the highest level. Since the freezer room adjacent to the room (freezer temperature zone room) is a storage room that is maintained at a low temperature, it is easy for food and the like in the freezer room to be heated due to the influence of the load flowing into the refrigerating room. That is, providing an air flow blocking means (insulation partition wall 28) for blocking the flow of air between the refrigerating air passage 111 and the frozen vegetable air passage 112 means that the refrigerating chamber (freezing temperature zone chamber) and the freezing chamber (freezing temperature zone chamber) are provided from above. This is especially effective for refrigerators that are arranged in the order of the freezing temperature zone room) and the vegetable room (refrigerating temperature zone room).

In the refrigerator of this embodiment, the refrigerating air passage 111 (first air passage) for circulating cooling air to the refrigerating chamber 2 (first refrigerating temperature zone chamber), which is a storage chamber having the maximum total circumference of the sealing member (packing), is used. ), And the freezer chamber 7 and the vegetable compartment 6 are provided with a frozen vegetable air passage 112 (second air passage) for circulating cooling air, and air that blocks the air flow between the refrigerated air passage 111 and the frozen vegetable air passage 112. It is provided with a distribution blocking means (insulation partition wall 28). A small gap may be created in the door seal due to the sandwiching of food or food packaging material, and the load may increase due to the inflow and outflow of outside air and storage room air. The longer the seal length between the door and the heat insulating box, that is, the longer the entire circumference of the seal member, the more likely it is that such a situation will occur. Therefore, the refrigerator of this embodiment is of the seal member (packing). A refrigerated air passage 111 that circulates cooling air to the refrigerating chamber 2, which is a storage chamber having the maximum total circumference, and a frozen vegetable style that circulates cooling air to the freezer chamber 7 and the vegetable compartment 6 located at the lower stage of the refrigerating chamber 2. By providing an air flow blocking means (insulating partition wall 28) that blocks the flow of air between the paths 112, other storage is affected by the load of the storage chamber that maximizes the total circumference of the sealing member (packing). It is possible to prevent the situation where the food in the room (freezer room or vegetable room) is heated, and the refrigerator has high cooling efficiency.

In the refrigerator of this embodiment, the maintenance temperature of the refrigerator compartment 2 is _{TR_keep (about 4 ° C. in the case of the setting "medium") and the maintenance temperature of the freezer compartment 7 is T F_keep (} setting "medium") during the stable cooling operation. In the case of about -20 ° C), assuming that the time average temperature of the refrigerating evaporator 14a during refrigerating operation is _{TRevp_ave} , the evaporator temperature adjusting means (compressor 24 and The rotation speed of the refrigerating fan 9a) is controlled.

Generally, in the refrigeration cycle, if the rotation speed of the compressor and the blower that blows air to the evaporator is controlled so that the time average temperature of the evaporator during the cooling operation is high, the refrigeration cycle coefficient of performance is improved and the cooling efficiency is improved. .. Therefore, raising the time average temperature of the evaporator when cooling the refrigerating chamber having a high temperature to be maintained is effective in improving the cooling efficiency. However, if there is a path through which the cooling air that cools the refrigerating chamber flows to the freezing chamber, the temperature of the freezing chamber that is maintained at a low temperature rises, so the time average temperature of the evaporator during refrigerating operation is sufficient. I couldn't make it higher. Therefore, the refrigerator of the present embodiment is provided with an air flow blocking means (insulation partition wall 28) for blocking the flow of air between the refrigerating air passage 111 and the frozen vegetable air passage 112, and also includes a compressor 24 and a refrigerating fan. By controlling the rotation speed of 9a, the time average temperature of the refrigerating evaporator during the refrigerating operation is sufficiently increased, and the relationship shown in (Equation 1) is satisfied, so that the refrigerator has high cooling efficiency. When there are a plurality of freezing chambers and the maintenance temperature thereof extends over a plurality of, the temperature of the storage chamber having the lowest temperature may be _{TF_keep} in (Equation 1).

In the refrigerator of this embodiment, the difference between the refrigerating chamber maintenance temperature _{TR_keep} and the time average temperature T _{Revp_ave} of the refrigerating evaporator 14a during the refrigerating operation is ΔT (= _{TR_keep} −T _{Revp_ave} ), and the evaporator. When the coefficient of performance of the refrigerating cycle theoretical performance with respect to the temperature is COP _th , the evaporator temperature adjusting means (compressor 24 and refrigerating fan 9a) is controlled so as to satisfy (Equation 2). As a result, the cooling operation can be efficiently performed within the range where the effectiveness of improving the air volume is high.

The reason will be described with reference to FIGS. 11 and 12. FIG. 11 (a) shows the relationship between the theoretical cycle coefficient of performance COP _th (coefficient of performance when the compressor efficiency is 100%) and the temperature of the refrigerator for refrigeration, and the difference between the refrigerating chamber maintenance temperature _{TR_keep} and the temperature of the evaporator T _evp . It is a graph which shows the inverse number ΔT ^-1 (= 1 / (T _{R_keep} －T _evp )) of. Further, FIG. 11 (b) shows a function (= d (COP _th ) / dT _ebp − d (ΔT ^-1 ) / dT _evp ) obtained by differentiating the difference between ΔT ^-1 and COP _th by the evaporator temperature T _evp . It is a graph.

Here, a method of obtaining the theoretical coefficient of performance COP _th shown in FIG. 11A will be described with reference to FIG. FIG. 12 is a Moriel diagram showing an operating state of a general refrigerator refrigeration cycle. The state (state 1) of the suction refrigerant of the compressor is determined by ignoring the pressure loss in the piping and keeping the pressure on the low pressure side (evaporator side) constant at the pressure determined by the evaporator temperature (evaporation temperature). On the high pressure side (condensor side), the outside air temperature is set as the condensation temperature (the temperature in the two-phase region), and the pressure is constant at the pressure determined by the condensation temperature. In addition, the refrigerant state at the condenser outlet (capillary tube inlet) is the saturated liquid (state 3), the refrigerant state at the evaporator outlet is saturated steam (state 5), and the capillary tube and the piping from the evaporator to the compressor are completely heated. The temperature of the compressor suction refrigerant is defined as the condenser outlet temperature (state 1) as a replacement (the action of the contact portion 57a in FIG. 4). In addition, by setting the efficiency of the compressor to 100% (adiabatic compression), the state of compressor discharge (state 2) is determined, and it is assumed that heat is completely exchanged between the capillary tube and the piping from the evaporator to the compressor (state 2). From Δh1 = Δh2) in FIG. 4, the refrigerant state (state 4) at the inlet of the evaporator is determined. By determining the outside air temperature and the evaporator temperature, the theoretical coefficient of performance COP _th is defined as the ratio of the theoretical cooling capacity Q _th and the theoretical compression power W _th (COP _th = Q _th / W _th ) based on the physical properties of the refrigerant. Can be calculated. This theoretical coefficient of performance COP _th is an index showing the cooling efficiency that does not depend on the efficiency of the compressor. The relationship between the theoretical coefficient of performance COP _th and the evaporator temperature T _evp shown in FIG. 11 (a) was calculated assuming that the refrigerant is isobutane and the outside air temperature T _out = 32 ° C.

In addition, in order to perform good cooling, it is necessary to obtain a predetermined amount of exchange heat in the evaporator. Ignoring changes in temperature efficiency (value obtained by dividing the difference between the evaporator inlet air temperature and the evaporator outlet air temperature by the difference between the evaporator inflow air temperature and the evaporator temperature), the air volume for obtaining a predetermined exchange heat amount is The relationship is derived that it is proportional to the inverse of the difference between the air temperature and the evaporator temperature. By using the refrigerating room maintenance temperature _{TR_keep} as the air temperature, ΔT ^-1 shown in FIG. 11 (a) is calculated, which is an index showing the magnitude of the air volume for obtaining a predetermined exchange heat amount. In addition, ΔT ^-1 shown in FIG. 11A is calculated assuming that the refrigerating chamber maintenance temperature _{TR_keep} is 4 ° C.

Both COP _th and ΔT ^-1 shown in FIG. 11 (a) increase monotonically with respect to the increase in the evaporator temperature T _evp , but their gradients are different. FIG. 11B is a function obtained by differentiating the difference between COP _th and ΔT ^-1 with the evaporator temperature T _evp , and shows the difference between the gradients of the two. That is, in the graph of FIG. 11B, in the range where the gradient is positive (the range where the evaporator temperature T _evp is lower than about -1 ° C.), the rate of increase in COP _th with respect to the increase in the evaporator temperature T _evp is higher. It can be said that it is advantageous to raise the evaporator temperature T _evp so as to improve the COP _th , which is higher than the rate of increase of ΔT ^-1 with respect to the rise of the evaporator temperature T _evp . On the other hand, in the range where the gradient is negative (the range where the evaporator temperature T _evp is higher than about -1 ° C), the rate of increase in COP _th with respect to the increase in the evaporator temperature T _evp is higher than the increase in the evaporator temperature T _evp . This indicates that the rate of increase is lower than that of ΔT ^-1 , and it can be said that the effectiveness of improving the air volume required to raise the evaporator temperature T _evp is decreasing. That is, control is performed so that d ² (COP _th ) / dT _ebp ² -d ² (ΔT ^-1 ) / dT _ebp ² ≧ 0 so that the graph in FIG. 11 (b) has a positive gradient range. This means that the refrigerator will be operated within the range where the effect of improving the air volume is high. Therefore, in the refrigerator of this embodiment, the evaporator temperature T _evp in FIG. 11 is controlled as the time average temperature T _{Revp_ave} of the refrigerating evaporator 14a during the refrigerating operation so as to satisfy (Equation 2). The cooling operation is efficiently carried out within the range where the effect of improving the air volume is high.

The refrigerator of this embodiment has an operation mode in which the drive time of the refrigerating fan 9a in the refrigerating chamber 2 having the maximum rated internal volume becomes longer than the driving time of the refrigerating fan 9b during the stable cooling operation. As a result, the refrigerating chamber 2 having the maximum rated internal volume can be made into a storage chamber with less temperature unevenness and high storage stability. Generally, the state in which an active airflow is generated by driving the blowing means is called forced convection, and the weak airflow generated by the temperature difference (density difference) of the air without being blown by the blowing means is called natural convection. When forced convection is generated in the space by the blowing means, the air actively moves to equalize the temperature in the space, and when the blowing means is stopped, natural convection occurs in the space. Since the movement of air is unlikely to occur, temperature unevenness is likely to occur, which is particularly noticeable in a space with a large volume. If the temperature unevenness is large, the problem that the food preservation property is deteriorated depending on the place where the food is stored tends to occur. Therefore, the refrigerator of this embodiment is provided with an operation mode in which the drive time of the refrigerating fan 9a in the refrigerating chamber 2 having the maximum rated internal volume is controlled to be longer than the driving time of the refrigerating fan 9b. The refrigerating room 2 is a storage room with little temperature unevenness and high storage stability.

Further, the refrigerator of the present embodiment has an operation mode in which the driving time of the refrigerating fan 9a of the refrigerating chamber 2, which is the storage chamber having the maximum height dimension, is longer than the driving time of the freezing fan 9b. In general, the temperature distribution tends to be larger in a space having a larger height dimension. Therefore, in the refrigerator of this embodiment, the driving time of the refrigerating fan 9a in the refrigerating chamber 2 which is the storage chamber having the maximum height dimension is set to the refrigerating fan. By providing an operation mode longer than the drive time of 9b, the refrigerating chamber 2 is made into a storage chamber with less temperature unevenness and high storage stability.

In the refrigerator of this embodiment, the refrigerating chamber discharge port 11a of the refrigerating chamber air passage 11 provided on the back surface of the refrigerating chamber is opened upward (cold air directing means) so that air directed upward is blown out. In general, when food stored in a storage chamber obstructs the flow of cooling air, temperature unevenness may occur in the storage chamber, or air passage resistance may increase and the air volume may decrease, resulting in a decrease in cooling efficiency. be. Therefore, by opening the main refrigerating chamber discharge port 11a of the refrigerating chamber air passage 11 upward (cold air directing means) and blowing out the air directed upward, the cooling air is shown by an arrow in FIG. Since it flows forward along the ceiling surface of the refrigerator compartment 2, even if many foods are stored in the refrigerator compartment 2, the flow of cooling air is less likely to be obstructed by the foods, and the temperature may be uneven in the storage chamber. ， It becomes a refrigerator with high cooling efficiency that is unlikely to cause a situation where the air passage resistance increases and the air volume decreases. In the refrigerator of this embodiment, the opening provided in the refrigerating chamber air passage 11 is only the refrigerating chamber discharge port 11a opened upward, but the refrigerator blows out toward the front or side. Other openings may be provided. In this case, the above-mentioned effect can be obtained by making the opening area (total area) of the discharge port opened upward larger than the total opening area of the other discharge ports.

The refrigerator of this embodiment is provided with a door pocket 33a having a higher opening position than the shelf 34a located at the uppermost stage of the refrigerating chamber 2, and the refrigerating chamber discharge port 11a of the refrigerating chamber air passage 11 provided on the back surface of the refrigerating chamber is upward. It is opened toward the air (cold air-oriented means) so that the air directed upward is blown out. As a result, as shown by the arrow in FIG. 2, the cooling air flows along the ceiling surface of the refrigerating chamber 2 toward the door pocket 33a whose opening position is higher than that of the shelf 34a located at the uppermost stage of the refrigerating chamber 2. The door pocket 33a can be cooled well.

In the refrigerator of this embodiment, the difference between the refrigerating room maintenance temperature (refrigerating room set temperature) _{TR_keep} and the refrigerating room discharge air temperature _{TR_in} discharged from the refrigerating room discharge port 11a during stable cooling operation is the freezing room maintenance temperature. _{TF_keep} (refrigerator room set temperature) and refrigerator room maintenance temperature (refrigerator room set temperature) Control the evaporator temperature adjusting means (compressor 24, refrigerating blower 9a) so that the temperature is higher than the arithmetic average value of _{TR_keep} . are doing. Generally, when low-temperature air is blown into a high-temperature space, the high-density low-temperature air receives a downward force due to the action of gravity, making it difficult for low-temperature air to reach the upper region away from the outlet. .. Therefore, in the refrigerator of this embodiment, the difference between the refrigerating room maintenance temperature (refrigerating room set temperature) TR_keep and the refrigerating room discharge air temperature _{TR_in} is the freezing room maintenance temperature TF_keep (refrigerating room setting temperature) and the refrigerating room maintenance temperature ( Refrigerator room set temperature) By controlling the evaporator temperature adjusting means (compressor 24, refrigerating blower 9a) so that it is higher than the arithmetic average value of _{TR_keep} , the cooling air blown out from the refrigerating room discharge port 11a is received. The action of gravity can be reduced, and the space above the discharge port (for example, the uppermost door pocket 33a) can be satisfactorily cooled.

The refrigerator of this embodiment includes a refrigerating room 2 (first refrigerating temperature zone room), a vegetable room 6 (second refrigerating temperature zone room), and a freezing room 7, and a refrigerating evaporator 14a is provided on the back of the refrigerating room 2. (First evaporator) and refrigerating blower 9a (first blower), refrigerating evaporator 14b (second evaporator) and refrigerating fan 9b (second blower) are provided on the back of the freezer chamber 7, and the first The refrigerating air passage 111 (first air passage) that circulates the cooling air that exchanged heat with the refrigerating evaporator 14a by driving the blower to the refrigerating chamber 2 and the refrigerating evaporator 14b by driving the refrigerating fan 9b exchanged heat. An air flow blocking means (air flow blocking means) provided with a frozen vegetable air passage 112 (second air passage) for circulating cooling air to the freezing chamber 7 and the vegetable chamber 6 and blocking the air flow between the first air passage and the second air passage. It is provided with a heat insulating partition wall 28) and a deodorizing member 91 in contact with the air flowing through the refrigerating air passage 111. As a result, when foodstuffs or the like that emit odor are stored in the refrigerating room 2, the odorous component can be prevented from circulating to other storage rooms (freezing room 7 and vegetable room 6) together with the cooling air, so that the refrigerating room 2 can be prevented. It is possible to prevent the transfer of odors to foodstuffs and the like in storage rooms (freezer room 7 and vegetable room 6) other than the above. Further, since the cooling air containing the odor component circulates only in the refrigerated air passage 111 and does not diffuse to other storage chambers, a high deodorizing effect can be obtained in a shorter time.

The refrigerator of this embodiment includes a refrigerated air passage 111 (first air passage), a frozen vegetable air passage 112 (second air passage), and a deodorizing member 91 in contact with the air flowing through the refrigerated air passage 111, and is provided with a stable cooling operation. It is provided with an operation mode in which the drive time of the refrigerating fan 9a in the refrigerating chamber 2 is longer than the driving time of the refrigerating fan 9b. When the refrigerating fan 9a is driven, more air passes through the deodorizing member 91, so that the deodorizing action is enhanced. Therefore, the refrigerating fan 9a has an operation mode in which the driving time of the refrigerating fan 9a is longer than that of the refrigerating fan 9b. As a result, the refrigerator can be made to have a higher deodorizing effect.

The refrigerator of this embodiment is provided with a storage chamber in the order of a refrigerating chamber 2 (first refrigerating temperature zone chamber), a freezing chamber 7 (freezing temperature zone chamber), and a vegetable compartment (second refrigerating temperature zone chamber) from above. A refrigerating evaporator 14b (second evaporator) is provided on the back of the refrigerator 7, the volume of the refrigerating evaporator 14b is set to 3% or less of the rated internal volume of the freezing chamber 7, and the rated internal volume of the freezing chamber 7 is the total rated content. A refrigerating evaporator 14a (first evaporator) is provided at the back of the refrigerating chamber 2 which is a refrigerating temperature zone chamber with 28% or more of the product. As a result, it is possible to provide a refrigerator having a large-capacity freezing chamber in the center of the refrigerator and exhibiting good practical cooling performance. The reason will be explained below.

Generally, frost grows on the surface of the evaporator that cools the freezing temperature zone chamber. When frost grows on the surface of the evaporator, the ventilation resistance increases due to the narrowing of the flow path through the evaporator, and the heat resistance increases due to the frost layer between the evaporator surface and the air, causing the heat of the evaporator. The replacement performance is reduced and the cooling efficiency is reduced. Therefore, the defrosting operation is performed so as not to cause a problem due to the deterioration of the heat exchange performance of the evaporator. The freezing temperature zone chamber cannot be cooled during the defrosting operation in which the frost is defrosted by raising the temperature of the evaporator by a heating means such as a heater. Therefore, if the heat exchange performance of the evaporator is likely to deteriorate due to the growth of frost, the defrosting operation in which the temperature of the freezing temperature zone chamber rises frequently is performed. In other words, making it difficult for the heat exchange performance to deteriorate due to the growth of frost is an issue for obtaining stable cooling performance in the freezing temperature zone chamber. For example, in a refrigerator having a cooler (evaporator) which is a heat exchanger for cooling each storage chamber in a cooling chamber (evaporator chamber) behind the freezer compartment, as in the refrigerator described in Patent Document 1. In general, the design is made so as to suppress the deterioration of heat exchange performance due to the growth of frost by making the size of the evaporator (evaporator volume) sufficiently large to solve this problem. On the other hand, the volume of the refrigerating evaporator cannot be reduced to 3% or less of the rated internal volume of the refrigerating temperature zone chamber, and the rated internal volume of the refrigerating temperature zone chamber cannot be expanded to 28% or more of the total rated internal volume. rice field.

Generally, the higher the air temperature, the larger the amount of water contained in the air (higher absolute humidity). Therefore, if an evaporator that cools the freezing temperature zone room and the refrigerating temperature zone chamber in common is provided, the freezing temperature zone chamber From the refrigerated temperature zone chamber, which has a higher maintenance temperature, more water reaches the evaporator and becomes frost. Therefore, the refrigerator of the present embodiment is provided with a refrigerating evaporator 14b on the back of the freezing chamber 7 and a refrigerating evaporator 14a on the back of the refrigerating chamber 2. Even if the evaporator installed on the back of the refrigerator 7 is downsized to 3% or less of the rated internal volume of the freezer chamber 7 and the rated internal volume of the freezer temperature zone chamber is expanded to 28% or more of the total rated internal volume, air will still be present. Since frost does not grow due to moisture from the refrigerator chamber 2 containing a large amount of water (absolute humidity), the evaporator is less likely to deteriorate in heat exchange performance and can exhibit stable cooling performance.

Further, the first evaporator is provided in the refrigerating temperature zone chamber having a large rated internal volume among the refrigerating chamber 2 and the vegetable chamber 6 which are the refrigerating temperature zone chambers. As a result, the refrigerating chamber 2 whose internal volume is large and the load tends to be large can be efficiently cooled, so that the refrigerator has both a large-capacity freezing chamber and good practical cooling performance.

In the refrigerator of this embodiment, the air-side heat transfer area A _Fevp of the refrigerating evaporator 14b is larger than the air-side heat transfer area A _Revp of the refrigerating evaporator 14a. In general, increasing the heat transfer area on the air side of the evaporator promotes heat exchange between the air and the refrigerant, and increases the cooling capacity. Therefore, the air-side heat transfer area A _Fevp of the refrigerating evaporator 14b is made larger than the air-side heat transfer area A _Revp of the refrigerating evaporator 14a to further enhance the cooling capacity when cooling the freezing chamber 7. ， Achieves both a large-capacity freezer and good practical cooling performance.

In the refrigerator of this embodiment, the heat transfer areas on the air side per unit volume of the refrigerating evaporator 14a and the refrigerating evaporator 14b are A _Revp / V _Revp = 0.673m ² / L and A _Fevp / V _Febp , respectively. = 0.384m ² / L, which is a value of 0.25m ² / L or more and 0.96m ² / L or less. In general, frost grows on the air-side heat transfer surface of the evaporator, so if the air-side heat transfer area is increased relative to the evaporator volume, the flow path is likely to be blocked when frost grows. Therefore, when the frost growth is large, the heat exchange performance is likely to deteriorate, but when the frost growth is small, the evaporator has high heat exchange performance. On the other hand, if the heat transfer area on the air side is made smaller than the volume of the evaporator, the flow path is less likely to be blocked by the frost even if frost grows, and it becomes easier to maintain heat exchange performance, but the heat transfer area on the air side becomes smaller. ， When the growth of frost is small, the heat exchange performance per unit volume becomes low. Therefore, in the refrigerator of this embodiment, the heat transfer area on the air side per unit volume of the refrigerating evaporator 14a and the refrigerating evaporator 14b is set to 0.25 m ² / L or more and 0.96 m ² / L or less. By doing so, it is possible to achieve both the performance when the frost growth is large and the performance when the frost growth is small.

Further, the air-side heat transfer area (A _Revp / V _Revp ) per unit volume of the refrigerating evaporator 14a is larger than the air-side heat transfer area (A _Fevp / V _Febp ) per unit volume of the refrigerating evaporator 14b. It is made larger (A _Revp / V _Revp > A _Fevp / V _Febp ). The frost grown on the refrigerating evaporator 14b is thawed by the refrigerating evaporator defrosting operation heated by the defrosting heater 21, and the freezing chamber 7 cannot be cooled during the refrigerating evaporator defrosting operation. On the other hand, the frost that has grown on the refrigerating evaporator 14a can be thawed while cooling the refrigerating chamber 2 by the refrigerating evaporator defrosting operation. Therefore, by making the air-side heat transfer area per unit volume of the refrigerating evaporator 14a larger than the air-side heat transfer area per unit volume of the refrigerating evaporator 14b, the flow path of the refrigerating evaporator 14b can be increased. It is difficult to be blocked by frost, and problems such as poor cooling of the freezer chamber 7 due to an increase in the frequency of defrosting operations are prevented from occurring.

In the refrigerator of this embodiment, when a practical load is applied to both the freezing temperature zone chamber and the refrigerating temperature zone chamber, the refrigerating chamber is cooled from the time when the load is applied until the practical load is sufficiently cooled. Evaporator temperature adjusting means (compressor 24, for refrigeration) so that the time average temperature T _{Revp_ave of the refrigerating evaporator 14a during operation is higher than the time average temperature T Fevp_ave of} the refrigerating evaporator 14b during freezing room cooling operation. The fan 9a, the refrigerating fan 9b, and the vegetable compartment damper 19) are controlled. Generally, the higher the evaporator temperature (evaporation temperature), the higher the refrigerating cycle coefficient of performance (ratio of the amount of heat absorbed to the input of the compressor 24), and the higher the energy saving performance. In the freezer chamber 7, it is necessary to lower the temperature of the refrigerating evaporator 14b in order to maintain the refrigerating temperature, but since the refrigerating chamber 2 may be maintained at the refrigerating temperature, the temperature T _Revp of the refrigerating evaporator is frozen. The temperature of the evaporator (compressor 24, refrigerating fan 9a, refrigerating fan 9b, vegetable compartment damper 19) is controlled so that the temperature is higher than the temperature T _Fevp of the refrigerator to improve the energy saving performance. ..

In the refrigerator of this embodiment, when a practical load is applied to both the freezing temperature zone chamber and the refrigerating temperature zone chamber, the maximum value (maximum reached temperature) of the freezing chamber temperature is less than 0 ° C. ( _TF1 <in FIG. 10). The evaporator temperature adjusting means (compressor 24, refrigerating fan 9a, refrigerating fan 9b, vegetable compartment damper 19) is controlled so as to be 0). As a result, good practical cooling performance can be obtained while avoiding the problem that the food or the like stored in the freezing temperature zone chamber is thawed due to the input of the practical load.

In the refrigerator of this embodiment, when a practical load is applied to both the freezing temperature zone chamber and the refrigerating temperature zone chamber, in the practical load cooling section from the time when the load is applied until the practical load is sufficiently cooled. The evaporator temperature adjusting means (compressor 24, refrigerating fan 9a, refrigerating fan 9b, vegetable compartment damper 19) is controlled so that a plurality of maximum values of the freezer temperature gradually decrease. As a result, the temperature of the freezing chamber rises, and the problem of melting frozen foods is unlikely to occur, resulting in a refrigerator with high practical cooling performance.

In the refrigerator of this embodiment, when a practical load is applied to both the freezing temperature zone chamber and the refrigerating temperature zone chamber, in the practical load cooling section from the time when the load is applied until the practical load is sufficiently cooled. Refrigerator room cooling operation ratio is _RR , freezer room cooling operation ratio is RF, outside air temperature is _{T out} (° C), air side heat transfer area of refrigerating evaporator 14a is A _Revp (m ² ), refrigerating evaporator. The time average temperature of 14a during refrigeration operation is TR _{evp_ave} (° C), the refrigerating room maintenance temperature is _{TR_keep} (° C), the air side heat transfer area of the refrigerating evaporator 14b is A _Fevp (m ² ), and the refrigerating evaporator. The time average temperature during the freezer compartment cooling operation of 14b is _{TFevp_ave} (° C), the freezer compartment maintenance temperature is _{TF_keep} (° C), the refrigerating chamber rated internal volume is _VR (L), and the freezer compartment rated internal volume is V _F (° C). L), the specific heat of water is C _W (kJ / kg ° C), the specific heat of ice is C _i (kJ / kg ° C), and the latent heat of solidification of water is L _W (kJ / kg), and (Equation 3) is satisfied. As described above, the evaporator temperature adjusting means (compressor 24, refrigerating fan 9a, refrigerating fan 9b, vegetable compartment damper 19) is controlled.

This results in a refrigerator that has both a large-capacity freezer and good practical cooling performance. The reason will be explained below. In general, in a refrigerator, not only heat intrusion through the wall surface of the heat insulating box, but also an unsteady increase in load such as a user's door opening / closing operation and input of hot food or the like occurs. In particular, in a refrigerator equipped with a storage room in the refrigerating temperature range and a storage room in the freezing temperature range, even if a situation occurs in which a large amount of food is put into both storage rooms at the same time, the temperature is quickly reached to the predetermined maintenance temperature. Need to cool down to. However, since the temperature zones to be maintained are different between the refrigerated temperature zone chamber and the freezing temperature zone chamber, it is easy for one storage chamber to be poorly cooled or only one storage chamber to be excessively cooled. In other words, the problem is to cool the refrigerated temperature zone room and the freezing temperature zone chamber in a well-balanced manner. Especially in a refrigerator equipped with a refrigerator compartment, a freezer compartment, and a vegetable compartment from above, the evaporator installed at the back of the freezer compartment is reduced to 3% or less of the rated internal volume of the freezer compartment to reduce the rated internal volume of the freezer compartment. If the capacity is increased to 28% or more of the total rated internal volume, the balance between the load of the refrigerator and the freezer and the cooling capacity will be lost, and one of the storage chambers will not cool well, or only one of the storage chambers will be excessively cold. The problem of cooling became apparent, and there was a situation in which good cooling performance could not be achieved. Therefore, in the refrigerator of this embodiment, when a practical load is applied to the refrigerating chamber 2 and the freezing chamber 7, the freezing operation / frozen vegetable operation and the refrigerating operation are performed so as to satisfy (Equation 3). Therefore, we are trying to achieve both a large-capacity freezer and practical cooling performance.
In (Equation 3), A _Fevp × ( _{TF_keep} -T _{Fevp_ave} ) is an index of the amount of exchanged heat in the refrigerating evaporator 14b, and A _Revp × ( _{TR_keep} -T _{Revp_ave} ) is an index of the amount of exchanged heat in the refrigerating evaporator 14a. , 12 × _VR × { _CW × (T _{out − TR_keep} )} is an index of the amount of heat absorption (cooling load) required for cooling the practical load put into the refrigerator compartment, and is 4 × _VF × {. C _W × T _out − C _i × _{TF_keep} + L _W } is an index of the amount of heat absorption (cooling load) required for cooling the practical load charged into the refrigerating chamber. That is, from the right side, the minimum required freezer room cooling (freezer room cooling operation or freezer room cooling operation) considering the ratio of the amount of heat exchanged between the refrigerating evaporator and the refrigerating evaporator and the ratio of the cooling load of the practical load. ) Is calculated as a ratio to the cooling room cooling operation. In the refrigerator of this embodiment, since the freezing room cooling operation is controlled so as to be higher than the ratio, a large capacity freezing is performed even when a large load is applied to the refrigerating room and the freezing room at the same time. It is possible to achieve both a room and practical cooling performance. The 12 × _VR and 4 × _VF on the right side of (Equation 3) are 12 g per 1 L of the refrigerated temperature zone chamber (freezing chamber and vegetable chamber) and 4 g of water per 1 L of the freezing temperature zone chamber (initial temperature is). It means that the outside air temperature) is put into the refrigerating room and the freezing room, respectively, and the load amount is defined in JISC9801-3: 2015 in consideration of general usage.
Further, since the refrigerator of this embodiment has an automatic ice making function, it is expected that the load will fluctuate when the user uses the automatic ice making function. In this case, since the ice making water tank is installed in the refrigerating chamber 2, the load on the refrigerating chamber 2 increases. However, since it does not freeze in the refrigerating chamber 2 maintained in the refrigerating temperature zone, it becomes a load of only sensible heat, and when water is supplied from the refrigerating chamber 2 to the ice making chamber 3 in the refrigerating temperature zone, it freezes and becomes sensible heat. In addition to that, latent heat is also a load. Therefore, since the load of the freezing chamber 7 is larger than that of the refrigerating chamber 2, the freezing temperature zone chamber is preferentially cooled by controlling as shown in (Equation 1), so that even when the automatic ice making function is used. ， It becomes easier to maintain practical cooling performance.

The refrigerating room maintenance temperature TR keep and the freezing room maintenance temperature _TF keep in (Equation 1) and (Equation 3) are the refrigerating room during stable cooling operation measured based on the method specified in JIS _C9801-1 : 2015. The time average value of the temperature of 2 and the freezer chamber 7 may be used. Further, the refrigerating evaporator temperature T _Revp and the refrigerating evaporator temperature T _Fevp for calculating the time average temperature ( _{TRevp_ave} , T _{Fevp_ave} ) of the refrigerating evaporator 14a and the refrigerating evaporator 14b are refrigerating evaporators. The temperature near the inflow portion of the refrigerant pipes 97a and 97b of the 14a and the refrigerating evaporator 14b may be measured and used.

The above is an example showing the embodiment of the present invention. The present invention is not limited to the above-mentioned examples, and includes various modifications. For example, in the refrigerator of this embodiment, a heat insulating partition wall 28 is adopted as an air flow blocking means in order to block the air flow more reliably, but if an action of blocking the air flow is obtained, the partition member A damper may be provided in a part of the above to block the air flow by closing the damper. Further, in the refrigerator of this embodiment, the compressor 24, the refrigerating fan 9a, and the refrigerating fan 9b are used as the evaporator temperature adjusting means, but if the evaporator temperature can be adjusted, the heat radiating means is used as another means. A fan that controls the amount of heat released from the refrigerator or an expansion valve that changes the throttle resistance may be used as an evaporator temperature adjusting means. That is, the above-mentioned examples have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the described configurations.

1 Refrigerator 2 Refrigerator room (1st refrigerating temperature zone room)
2a, 2b Refrigerator room door 3 Ice making room 4 Upper freezer room 5 Lower freezer room Freezer room 3a, 4a, 5a Freezer room door 6 Vegetable room (second refrigerating temperature zone room)
6a Vegetable room door 7 Freezing room (general term for 3, 4, 5)
8a Refrigerator evaporator room (first evaporator storage room)
8b Freezing evaporator room (second evaporator storage room)
9a Refrigerator fan (first blower)
9b Freezing fan (second blower)
10 Insulated box body 10a Outer box 10b Inner box 11 Refrigerator room air passage 11a Refrigerator room air outlet 12 Freezer room air passage 12a Freezer room air outlet 13 Vegetable room air passage 13a Vegetable room air outlet 14a Refrigerator evaporator (first evaporator) )
14b Freezing evaporator (second evaporator)
15a, 15b 15c Refrigerator room return air passage 16 Hinge cover 17 Freezer room return port 18 Vegetable room return air passage 18a Vegetable room return port 19 Vegetable room damper 21 Radiant heater 22a, 22b Drain port 23a, 23b Gutter 24 Compressor 26 Outside Fan 27a Refrigerator drain pipe 27b Refrigerator drain pipe 28, 29, 30 Insulation partition wall 31 Control board 32 Evaporator 35 Chilled room 39 Machine room 40a Refrigerator evaporator temperature sensor 40 b Refrigerator evaporator temperature sensor 41 Refrigerator chamber temperature sensor (First load detection means)
42 Freezing room temperature sensor (second load detecting means)
43 Vegetable room temperature sensor 50a, 50b External radiator (heat dissipation means)
50c Dew condensation suppression piping (heat dissipation means)
51 Dryer 52 Three-way valve (refrigerant control means)
53a Refrigerating capillary tube (decompression means)
53b Freezing capillary tube (decompression means)
54a Air-liquid separator for refrigeration 54b Air-liquid separator for refrigeration 55a, 55b Heat exchange part 56 Check valve 91 Deodorizing member 95a, 95b Refrigerating chamber packing (first seal member)
96a, 96b, 96c Freezing chamber packing (second seal member)
97 Vegetable room packing (third seal member)
101 Gutter heater 102 Drainage pipe upper heater 103 Drainage pipe lower heater

Claims (2)

The first storage chamber, the second storage chamber, and the third storage chamber are provided in the heat insulating box from above, and the first evaporator and the first storage chamber are provided in the area where the first storage chamber is partitioned inside the heat insulating box. An air blower is provided, and a second evaporator and a second blower are provided in the area where the second storage chamber or the third storage chamber is partitioned, and the air exchanged heat with the first evaporator by driving the first blower. The first air passage that circulates the air to the first storage chamber and the second air passage that circulates the air that has exchanged heat with the second evaporator by driving the second blower to the second storage chamber and the third storage chamber. An air flow blocking means for blocking the flow of air between the first air passage and the second air passage is provided, and defrosted water from the first evaporator is placed in the lower part of the first evaporator. It is equipped with a receiving gutter and a gutter heater for heating the gutter, and the return air from the first storage chamber is applied to the gutter with respect to the first air passage.
By controlling at least the compressor and the first blower, the time average temperature of the first evaporator during the refrigerating operation in the stable cooling operation can be controlled by the maintenance temperature of the second storage chamber and the maintenance of the first storage chamber. A refrigerator characterized in that the temperature is equal to or higher than the arithmetic mean value and lower than about -1 ° C. The first storage chamber, the second storage chamber, and the third storage chamber are provided in the heat insulating box from above, and the first evaporator and the first storage chamber are provided in the area where the first storage chamber is partitioned inside the heat insulating box. An air blower is provided, and a second evaporator and a second blower are provided in the area where the second storage chamber or the third storage chamber is partitioned, and the air exchanged heat with the first evaporator by driving the first blower. The first air passage that circulates the air to the first storage chamber and the second air passage that circulates the air that has exchanged heat with the second evaporator by driving the second blower to the second storage chamber and the third storage chamber. An air flow blocking means for blocking the flow of air between the first air passage and the second air passage is provided, and defrosted water from the first evaporator is placed in the lower part of the first evaporator. It is equipped with a receiving gutter and a gutter heater for heating the gutter, and the return air from the first storage chamber is applied to the gutter with respect to the first air passage.
By controlling at least the compressor and the first blower, the difference between the maintenance temperature TR_keep of the first storage chamber and the time average temperature TRevp_ave of the first evaporator during the refrigerating operation in the stable cooling operation is ΔT (=). TR_keep-TRevp_ave), and the refrigerator is characterized by satisfying the following equation when the refrigeration cycle theoretical coefficient of performance with respect to the evaporator temperature is COPth.

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