JP2019132497A - refrigerator - Google Patents

Abstract

To provide a refrigerator capable of exerting high cooling efficiency in the whole refrigerator even when a load of a part of storage chambers is increased, in the refrigerator including a refrigeration chamber, a freezing chamber and a vegetable chamber.SOLUTION: A refrigerator including a first refrigeration temperature zone chamber, a second refrigeration temperature zone chamber, and a freezing temperature zone chamber, and further including a first evaporator and a first blower at a back part of the first refrigeration temperature zone chamber, and a second evaporator and a second blower at a back part of the freezing temperature zone chamber or the second freezing temperature zone chamber, further includes a first air channel for circulating air exchanging heat with the first evaporator by driving the first blower, to the first refrigeration temperature zone chamber, and a second air channel for circulating air exchanging heat with the second evaporator by driving the second blower to the freezing temperature zone chamber and the second refrigeration temperature zone chamber, and air circulation block means is disposed to block circulation of the air between the first air channel and the second air channel.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a refrigerator.

  As a background art in this technical field, for example, there is JP-A-2006-64256 (Patent Document 1).

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

JP 2006-64256 A

  The refrigerator described in Patent Document 1 includes a refrigerator compartment, a freezing temperature compartment (ice compartment, select compartment, freezer compartment), and a vegetable compartment. The refrigerator compartment cools the refrigerator compartment by using the evaporator for the refrigerator compartment. Thus, the ice room, select room and freezer room are cooled, and the vegetable room provided below the freezer room is indirectly cooled with the cooling air of the freezer room through a partition wall between the freezer room and the like.

  When cooling indirectly, it is necessary to promote heat transfer through the partition walls in order to increase the cooling capacity of the vegetable compartment. In general, it is effective to increase the temperature difference between the spaces (freezer compartment and vegetable compartment) separated by the partition walls in order to promote heat transfer through the partition walls. Therefore, the load on the vegetable compartment may be reduced due to reasons such as high ambient temperature, food containing high temperature in the vegetable compartment, or a gap between the vegetable compartment door and the heat insulation box due to food being sandwiched. When the cooling capacity is large enough, it is necessary to keep the freezer room at an excessively low temperature, resulting in a decrease in cooling efficiency. In addition, the refrigerator compartment in contact with the freezer compartment also has a problem in that the cooling efficiency is lowered due to the heat effect of the freezer compartment indirectly by keeping the freezer compartment at an excessively low temperature. That is, in order to cool the load of some storage rooms, the problem that the cooling efficiency as the whole refrigerator fell occurred.

  The present invention has been made in view of the above problems, and in a refrigerator having a refrigerator compartment, a freezer compartment, and a vegetable compartment, even if the load on some storage compartments becomes large, It aims at providing the refrigerator which can exhibit 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-described problems. For example, the first refrigeration temperature zone chamber, the second refrigeration temperature zone chamber, and the refrigeration temperature zone chamber include the first refrigeration temperature zone chamber. In the refrigerator provided with the first evaporator and the first blower on the back portion and the second evaporator and the second blower on the back portion of the freezing temperature zone chamber or the second refrigeration temperature zone chamber, by driving the first blower A first air passage through which the air heat-exchanged with the evaporator flows through the first refrigeration temperature zone chamber; and air that has exchanged heat with the second evaporator by driving the second blower. And a second air passage that circulates in the two refrigerated temperature zone chambers, and further includes an air circulation blocking means that interrupts the air flow between the first air passage and the second air passage.

  According to the present invention, in a refrigerator having 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 on some storage compartments is increased. Can be provided.

Front view of the refrigerator according to the embodiment AA sectional view of FIG. BB sectional view of FIG. The schematic diagram showing the air path structure of the refrigerator which concerns on an Example. Schematic showing the refrigerating cycle structure of the refrigerator which concerns on an Example. The figure showing the evaporator of the refrigerator which concerns on an Example The flowchart showing the normal operation control of the refrigerator which concerns on an Example. The flowchart showing the operation control at the time of high load of the refrigerator which concerns on an Example. An example of a time chart representing normal control of the refrigerator according to the embodiment An example of a time chart representing control at high load of the refrigerator according to the embodiment Graph showing the relationship between the evaporator temperature, the coefficient of theoretical performance, and the refrigerator temperature Mollier diagram showing the state of the refrigeration cycle of the refrigerator

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

  An embodiment of the refrigerator according to the present invention will be described. First, the structure of the refrigerator which concerns on an Example is demonstrated, referring FIGS. 1 is a front view of a refrigerator according to the embodiment, FIG. 2 is a sectional view taken along line AA in FIG. 1, FIG. 3 is a sectional view taken along line BB in FIG. FIG. 5 is a schematic diagram illustrating the configuration of the refrigeration cycle of the refrigerator according to the embodiment. The heat insulating box 10 of the refrigerator 1 is opened forward, and from above the refrigerator compartment 2 (first refrigerator temperature zone), the ice making compartment 3 and the upper freezer compartment 4, the lower freezer compartment 5, arranged side by side on the left and right. A storage room is formed in the order of the vegetable room 6 (second refrigeration temperature zone room). Hereinafter, the ice making room 3, the upper freezing room 4, and the lower freezing room 5 are collectively referred to as a freezing room 7 (freezing temperature zone room).

  The front opening of the refrigerating room 2 is opened and closed by 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 The drawer-type ice making room door 3a, the upper freezer compartment door 4a, the lower freezer compartment door 5a, and the vegetable compartment door 6a are opened and closed. Refrigerator compartment packings 95a and 95b (first seal members), ice making door 3a, upper freezer compartment door 4a, and lower freezer compartment door 5a are provided on the outer perimeter of refrigerator compartment doors 2a and 2b. Is a freezer compartment packing 96a, 96b, 96c (second seal member) as a seal member, and a vegetable compartment packing 97 (third seal member) as a seal member on the inner periphery of the vegetable compartment door 6a which is a door of the vegetable compartment 6. When the doors are closed, the flow of air inside and outside the cabinet is suppressed by contacting the front edge of the heat insulating box 10. The peripheral lengths of the refrigerator compartment packings 95a and 95b are 2271 mm and 2441 mm, respectively, and the total peripheral length of the refrigerator compartment packings 95a and 95b (peripheral length of the first seal member) is 4712 mm. The peripheral lengths of the freezer compartment packings 96a, 96b, and 96c are 976 mm, 1416 mm, and 2087 mm, respectively, and the total peripheral lengths of the freezer compartment packings 96a, 96b, and 96c (the peripheral length of the second seal member) are 4209 mm. Moreover, the perimeter of the vegetable compartment packing 97 (perimeter of the third seal member) is 2107 mm. The open / close states of the refrigerator compartment doors 2a and 2b, the ice making compartment door 3a, the upper freezer compartment door 4a, the lower freezer compartment door 5a, and the vegetable compartment door 6a are close to each door and the front edge of the heat insulating box 10. It is detected by a door sensor (not shown) that detects.

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

  The temperature of the refrigerator compartment 2 and the temperature of the freezer compartment 7 can be selected by the user via the operation unit 99. Specifically, the setting of the maintenance temperature level of the refrigerator compartment 2 and the freezer compartment 7 can be set in three stages of “strong”, “medium”, and “weak”, respectively. 2 ° C, “Medium” is maintained at about 4 ° C., “Low” is maintained at about 6 ° C., and the freezer room 7 is “High” at about −22 ° C., “Medium” is about −20 ° C., “Low” is about − Maintained at 18 ° C. The vegetable room 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 refrigerating chamber height _{H R} is _H R = _787mm, freezing chamber height _{H F} is _H F = 482mm, vegetable compartment height _{H V} is _H V = 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 refrigerator compartment 2 (refrigerated compartment rated internal volume) is 308L, 51.2% of the total rated internal volume, The rated internal volume (freezer compartment rated internal volume) is 180L, 29.9% (28% or more of the total rated internal volume), the vegetable room 6 rated internal volume (vegetable room rated internal volume) is 114L, and all rated contents 18.9% of the product.

  As shown in FIG. 2, the outside of the refrigerator 1 and the inside of the refrigerator 1 are separated by a heat insulating box 10 formed by filling a foam heat insulating material (for example, urethane foam) between the outer box 10 a and the inner box 10 b. ing. In addition to the foam heat insulating material, a plurality of vacuum heat insulating materials 36 are mounted on the heat insulating box 10 between a steel plate outer box 10a and a synthetic resin inner box 10b. The refrigerator compartment 2, the upper freezer compartment 4 and the ice making compartment 3 are separated by a heat insulating partition wall 28 (air circulation blocking means), and the lower freezer compartment 5 and the vegetable compartment 6 are separated by a heat insulating partition wall 29. In addition, a heat insulating partition wall is provided on the front side of each storage room of the ice making room 3, the upper freezing room 4, and the lower freezing room 5 in order to prevent the flow of air inside and outside the space through the gaps of the doors 3a, 4a, 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 on the inner side of the doors 2a, 2b of the refrigerator compartment 2 and 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. The freezer compartment 7 and the vegetable compartment 6 are respectively provided with an ice making container (not shown), an upper freezer container 4b, a lower freezer container 5b, and a vegetable compartment container 6b that are pulled out integrally with the doors 3a, 4a, 5a, 6a. I have. The vegetable compartment container 6b is divided into two upper and lower tiers, and a bottle storage space 6c is provided in front of the lower tier for storing beverage bottles. The height of the bottle storage space 6c is 305 mm or more (315 mm in this embodiment) so that 1.5L and 2L beverage bottles can be stood and stored. Also, the ability to store beverage bottles is made known to users through catalogs, instruction manuals, texts such as advertising media, diagrams, photographs, and videos.

  A chilled room 35 that can be set lower than the temperature range of the refrigerator compartment 2 is provided above the heat insulating partition wall 28. In the chilled room 35, the user can select a set temperature via the operation unit 99. Specifically, it can be set to either “temperature level 1” maintained at about 0 to 3 ° C. of the refrigeration temperature zone or “temperature level 2” maintained at about −3 to 0 ° C. of the refrigeration temperature zone. it can.

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

  A refrigeration evaporator chamber 8a is provided substantially at the back of the refrigeration chamber 2, and a refrigeration evaporator 14a (first evaporator), which is a fin-tube heat exchanger, is accommodated in the refrigeration evaporator chamber 8a. Has been. A refrigeration fan 9a (first blower) is provided above the refrigeration evaporator 14a. Further, a refrigerator compartment air passage 11 is provided at a substantially center in the width direction of the back of the refrigerator compartment 2, and a refrigerator outlet having an orientation means for directing the air to be blown upward is provided above the refrigerator compartment air passage 11. 11a. In the refrigerator of the present embodiment, the opening surface of the refrigerator compartment discharge port 11a is directed upward as the directing means of the refrigerator compartment 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 shelf 34a. , 34b, 34c flows through the gaps between the door pockets 33a, 33b, 33c, and the chilled room 35 through an opening 92 (see FIG. 3) provided at the left rear of the space between the shelf 34c and the shelf 34d. To the refrigeration evaporator chamber 8a from the refrigeration chamber return air passages 15a, 15b, 15c (see FIG. 3) provided on the lower front surface, the lower left surface, and the lower right front surface of the refrigeration evaporator chamber 8a. Return. Further, a part of the air flowing through the space between the shelf 34c and the shelf 34d is used for refrigeration from the refrigerator compartment return air passage 15d (see FIG. 3) provided at the right rear of the space between the shelf 34c and the shelf 34d. Return to the evaporator chamber 8a. A part of the refrigerating room return air passage 15c is provided with a deodorizing member 91 (open cell structure deodorizing member as an example) so as to be in contact with the air flowing through the refrigerating room 2.

  A refrigeration evaporator chamber 8b is provided substantially at the back of the freezer compartment 7, and a refrigeration evaporator 14b (second evaporator), which is a fin-tube heat exchanger, is accommodated in the refrigeration evaporator chamber 8b. Has been. A freezing fan 9b is provided above the freezing evaporator 14b. A freezer compartment air passage 12 is provided at the back of the freezer compartment 7, and a plurality of freezer compartment discharge ports 12 a are provided in the freezer compartment air passage 12 in front of the freezing fan 9 b (second blower). A freezer compartment return air passage 17 (see FIGS. 2 and 3) through which air sent to the freezer compartment 7 returns is provided in front of the lower part of the freezer compartment evaporator chamber 8b.

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

  Next, the air path configuration of the refrigerator according to the present embodiment will be described with reference to FIG. The air that has become low temperature by exchanging heat with the refrigeration evaporator 14a is sent to the refrigeration room 2 via the refrigeration room air passage 11 and the refrigeration room discharge port 11a by driving the refrigeration fan 9a. 2 is cooled. 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 refrigeration evaporator chamber 8a through the refrigeration chamber 2 and returns to the refrigeration evaporator chamber 8a is referred to as a refrigeration air passage 111 (first air passage). In addition, the air that has become low temperature by exchanging heat with the freezing evaporator 14b is sent to the freezing room 7 through the freezing room air passage 12 and the freezing room discharge port 12a by driving the freezing fan 9b. The inside of the freezer compartment 7 is cooled. The air sent to the freezer compartment 7 returns from the freezer compartment return air passage 17 to the freezer evaporator chamber 8b. In addition, when the vegetable compartment damper 19 is in an open state, a part of the cooling air flowing into the freezer compartment air passage 12 flows through the vegetable compartment air passage 13 and reaches the vegetable compartment 6 through the vegetable compartment discharge port 13a. Cool 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 compartment 8b. Hereinafter, an air path that flows from the freezing evaporator chamber 8b through the freezing chamber 7 and returns to the freezing evaporator chamber 8b, and an air flow 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 path 112 (second air path).

  In the refrigerator of the present embodiment, the refrigeration fan 9a is a centrifugal fan (backward fan) having a blade diameter of 100 mm, and the refrigeration fan 9b is an axial fan (propeller fan) having a blade diameter of 110 mm. The centrifugal fan has a characteristic that the air sucked from the axial direction is turned 90 degrees and blown out in the radial direction. On the other hand, the axial fan has a characteristic of blowing out air sucked from the axial direction in the axial direction. Therefore, the centrifugal fan is excellent in mountability in the air passage that turns the flow sucked in the axial direction by 90 degrees, and the axial fan is excellent in mountability in the air passage that blows out the flow sucked in the axial direction in the axial direction. Accordingly, since the refrigeration fan 9a is configured to turn the air sucked from the front 90 degrees and blow it out to the upper refrigeration chamber air passage 11, a rearward fan, which is a centrifugal fan, is adopted as the refrigeration fan 9b. Has a configuration in which the air sucked from the rear is blown out to the front freezer compartment air passage 12, so that a propeller fan, which is an axial fan, is used to provide a highly space-efficient refrigerator.

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

  In addition, a defrosting heater 21 for heating the freezing evaporator 14b is provided below the freezing evaporator chamber 8b. The defrost heater 21 is, for example, an electric heater of 50 W to 200 W, and a 150 W radiant heater is provided in this embodiment. The defrost water (melted water) generated when the refrigeration evaporator 14b is defrosted flows down to the tub 23b provided at the lower part of the refrigeration evaporator chamber 8b, and is stored in the refrigerator via the drain port 22b and the refrigeration drain pipe 27b. 1 reaches the machine room 39 provided at the lower part of the rear (back side), and is discharged to the evaporating dish 32 above the compressor 24 installed in the machine room 39.

  Further, although a defrosting method for the refrigeration evaporator 14a will be described later, the defrost water generated at the time of defrosting the refrigeration evaporator 14a flows down to the tub 23a provided in the lower part of the refrigeration evaporator chamber 8a. It is discharged to the evaporating dish 32 provided on the upper part of the compressor 24 through the drain port 22a and the refrigeration drain pipe 27a.

  In the machine room 39, the above-described compressor 24 and evaporating dish 32 are provided, as well as an outside heat radiator 50a and an outside fan 26 that are fin-tube heat exchangers. By driving the external fan 26, air flows into the compressor 24 and the external radiator 50a evaporating dish 32, heat dissipation from the compressor 24 and the external radiator 50a is promoted, energy saving performance is improved, and By ventilating, the evaporation of defrosted water accumulated in the evaporating dish 32 is promoted to suppress overflow and improve reliability.

  As shown in FIG. 3, the eaves 23 a includes an eaves heater 101 that melts the defrost water frozen in the eaves 23 a. The refrigeration drain pipe 27 a includes a drain pipe upper heater 102 and a drain pipe lower heater 103. The dredge heater 101, the drain pipe upper heater 102, and the drain pipe lower heater 103 are all heaters having a capacity lower than that of the defrost heater 21. In this embodiment, the dredge heater 101 is 6 W and the drain pipe upper heater 102 is 3W, drain pipe lower heater 103 is 1W.

  Here, when the refrigeration fan 9a is driven, the return air from the refrigeration chamber 2 flows downward toward the tub 23a through the refrigeration chamber return port 15b provided at the upper right of the refrigeration evaporator chamber 8a. 23a is heated to raise the temperature. Thereby, the effect of reducing the heating amount of the firewood heater 101 that melts the defrosted water frozen in the firewood 23a is obtained, and the energy saving performance can be enhanced.

  The lower part of the drain pipe 27a is closer to the outer box 10a than the freezer compartment 7 and the freezer evaporator compartment 8b. Thereby, the heating amount of the drain pipe lower heater 103 for melting the defrost water frozen in the drain 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 and a RAM, an interface circuit, etc., which are a part of the control device are mounted. The control board 31 is connected to the refrigerator compartment temperature sensor 41, the freezer compartment temperature sensor 42, the vegetable compartment temperature sensor 43, the evaporator temperature sensors 40a, 40b, etc., and the CPU described above sets these output values and the operation unit 99. , Based on a program or the like recorded in advance in the ROM, the compressor 24, the refrigeration fan 9a, the refrigeration fan 9b ON / OFF and the rotational speed control, the defrost heater 21, the soot heater 101, the drain pipe upper heater 102, the drain pipe lower heater 103, and a three-way valve 52, which will be described later, are controlled.

  FIG. 5 is a refrigeration cycle (refrigerant flow path) of the refrigerator according to the first embodiment. In the refrigerator 1 of the present embodiment, the compressor 24 (pushing amount 9.2 cc), the external heat radiator 50a that radiates the refrigerant, the wall surface heat radiating pipe 50b, and the front edges of the heat insulating partition walls 28, 29, and 30 are provided. Condensation suppression piping 50c that suppresses condensation (external heat radiator 50a, external heat radiator 50b, and condensation suppression piping 50c are referred to as heat dissipation means), a three-way valve 52 that is a refrigerant flow control means, and a pressure reduction means that decompresses the refrigerant. A refrigeration capillary tube 53a, a refrigeration capillary tube 53b, a refrigeration evaporator 14a that absorbs heat in the refrigerator by exchanging heat between the refrigerant and the air in the refrigerator, and a refrigeration evaporator 14b are provided. Further, a dryer 51 for removing moisture in the refrigeration cycle is provided upstream of the three-way valve 52, and liquid refrigerant is supplied to the compressor 24 downstream of the refrigeration evaporator 14a and downstream of the refrigeration evaporator 14b, respectively. A refrigeration gas / liquid separator 54a and a refrigeration gas / liquid separator 54b for preventing the inflow are provided. Further, a check valve 56 is provided downstream of the refrigeration gas-liquid separator 54b. A refrigeration cycle is configured by connecting these components through refrigerant piping. In the refrigerator of this embodiment, the temperature of the refrigeration evaporator 14a and the refrigeration evaporator 14b is adjusted by the rotational speed of the compressor 24, the refrigeration fan 9a, and the refrigeration fan 9b. The fan 9a and the refrigerating fan 9b are referred to as evaporator temperature adjusting means. In addition, flammable refrigerant isobutane is used as the refrigerant, and the amount of refrigerant enclosed is 88 g.

  The three-way valve 52 includes an outflow port 52a and an outflow port 52b. With the outflow port 52a in an open state and the outflow port 52b in a closed state, the refrigerant flows into the chilling capillary tube 53a side 1 (refrigeration mode), State 2 (freezing mode) in which the outlet 52a is closed and the outlet 52b is opened, and the refrigerant flows to the freezing capillary tube 53b side, and state 3 (all the outlets 52a and 52b are closed) (Closed mode).

  When the three-way valve 52 is controlled in the state 1 (refrigeration mode), the refrigerant discharged from the compressor 24 flows through the external heat radiator 50a, the external heat radiator 50b, and the dew condensation suppression pipe 50c to radiate heat, and the dryer 51 To the three-way valve 52. Since the three-way valve 52 is in the state 1 (the outlet 52a is in the open state and the outlet 52b is in the closed state), the refrigerant flows through the refrigeration capillary tube 53a and is depressurized to reach the refrigeration evaporator 14a. Heat exchange with the return air of the refrigerator compartment 2 is performed. The refrigerant that has exited the refrigeration evaporator 14a passes through the refrigeration 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 external heat radiator 50a, the external heat radiator 50b, and the dew condensation suppression pipe 50c to radiate heat, and the dryer 51 To the three-way valve 52. Since the three-way valve 52 is in the state 2 (the outlet 52a is closed and the outlet 52b is open), the refrigerant flows through the refrigeration capillary tube 53b to be depressurized and reduced in temperature. In 14b, heat exchange is performed with the return air of the freezer compartment 7 and the return air of the vegetable compartment 6 (when the vegetable compartment damper 19 is in an open state). The refrigerant exiting the refrigeration evaporator 14b passes through the refrigeration 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 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 refrigeration capillary tube 53a and the freezing capillary tube 53b. The refrigerant in 14a or the refrigerant in the refrigeration evaporator 14b is collected 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 be in state 1 (refrigeration mode), the compressor 24 is driven, the refrigeration fan 9a is driven, and the refrigeration fan 9b is stopped. “Refrigeration operation” for cooling the refrigerator, the three-way valve 52 is controlled to state 2 (freezing mode), the compressor 24 is driven, the vegetable compartment damper 19 is opened, the refrigeration fan 9a is driven or stopped, "Frozen vegetable operation" that cools the freezer compartment 7 and the vegetable compartment 6 by setting the fan 9b in the driving state, the three-way valve 52 is controlled to the state 2 (freezing mode), the compressor 24 is driven, and the vegetable compartment damper 19 is closed, refrigeration fan 9a is driven or stopped, and refrigeration fan 9b is driven to “freeze operation” to cool freezer compartment 7, and three-way valve 52 is set to state 3 (fully closed mode). Control and drive compressor 24 "Refrigerant recovery operation" in which the refrigerant in the refrigeration evaporator 14a or the refrigerant in the refrigeration evaporator 14b is recovered to the heat radiating means side, and the three-way valve 52 is in state 3 (fully closed mode). “Stop operation” in which the refrigeration fan 9a is stopped and the refrigeration fan 9b is stopped, the three-way valve 52 is controlled to the state 2 (refrigeration mode) and the compressor 24 is driven, or the three-way valve 52 is stopped. Is controlled in the state 3 (fully closed mode) and the compressor 24 is stopped, and the refrigerant is not flown into the refrigeration evaporator 14a, the refrigeration fan is driven, and it has grown on the surface of the refrigeration evaporator 14a. Compressor with refrigeration evaporator defrosting operation to defrost refrigeration evaporator 14a while refrigeration chamber 2 is cooled with frost or cold storage heat of evaporator itself, with three-way valve 52 in state 3 (fully closed mode) 24 is stopped, refrigeration fan Each operation of “refrigeration evaporator defrosting operation” for defrosting the refrigeration evaporator 14b by setting “a” to a drive state or a stop state, the refrigeration fan 9b to a stop state, and the defrost heater 21 to be energized. As appropriate, each storage room in the refrigerator 1 is cooled.

  The interval (defrost interval) at which the refrigeration evaporator defrosting operation is performed is variable between a maximum of 96 hours (maximum defrost interval) and a minimum of 12 hours (shortest defrost interval). Specifically, the outside air temperature and humidity detected by the outside air temperature and humidity sensor 37, the number of times the doors 3a, 4a, 5a and 6a are opened and closed, the rotation speed of the compressor during the freezing operation and the frozen vegetable operation, and the freezing evaporator temperature sensor 40b The defrost interval is determined based on the detected refrigeration evaporator temperature, the outside air temperature is high, the outside air humidity is high, the freezer compartment door is opened and closed frequently, the compressor rotation speed during freezing operation and frozen vegetable operation is The interval becomes shorter as the minimum temperature of the evaporator temperature for freezing operation and frozen vegetable operation is lower. In this way, by changing the interval of the refrigeration evaporator defrosting operation, when the frost grows on the refrigeration evaporator 14b, the refrigeration evaporator defrosting operation can be performed at an appropriate timing. The heat exchange efficiency of the refrigeration evaporator is greatly reduced, and good practical cooling performance can be demonstrated. In addition, by setting the longest defrosting interval, a reliable refrigeration evaporator defrosting operation is performed periodically. Thereby, in particular, unintended frost growth on the wall surface of the refrigeration evaporator chamber 8b other than the refrigeration evaporator 14b can be suppressed, and reliability is improved. Moreover, since the freezer compartment 7 cannot be cooled during the freezing evaporator defrosting operation, the temperature of the freezer compartment 7 rises. In the refrigerator of the present embodiment, by providing the shortest defrosting interval, the defrosting interval is prevented from becoming too short, and the temperature of the freezing room 7 is not frequently increased by the defrosting operation so that the frozen food can be dissolved. The refrigerator is less likely to cause problems.

  When the refrigerant in the refrigeration evaporator 14a is recovered to the heat radiating means side, the refrigeration fan 9a is driven, and when the refrigerant in the refrigeration evaporator 14b is recovered to the heat radiating means side, The fan 9b is driven to cool the refrigerator compartment 2 and the freezer compartment 7 even during the refrigerant recovery operation (details will be described later). Therefore, the “refrigeration operation” in which the cooling chamber 2 is cooled and the refrigerant recovery operation for recovering the refrigerant in the refrigeration evaporator 14a are collectively referred to as “refrigeration chamber cooling operation”. A general term of the “frozen vegetable operation” and “refrigeration operation” and the refrigerant recovery operation that recovers the refrigerant in the freezing evaporator 14b is called “freezer compartment cooling operation”.

FIG. 6 is a view showing an evaporator of the refrigerator according to the present embodiment, FIG. 6 (a) is a refrigeration evaporator 14a, and FIG. 6 (b) is a refrigeration evaporator. As shown in FIG. 6A, the refrigeration evaporator 14a is a fin-tube heat exchanger in which aluminum fins 98a are attached to an aluminum refrigerant pipe 97a. The refrigerant, which has been decompressed by the refrigeration capillary tube 53a (see FIG. 5) and has become low temperature and low pressure, flows through the refrigerant pipe 97a and returns from the refrigerating chamber 2 flowing in from the lower front of the refrigeration evaporator 14a (see FIG. 2 or 3) and heat exchange via the fins 98a and the surface of the refrigerant pipe 97a. The fins 98a are divided into three stages in the height direction, and two stages of refrigerant pipes 97a are provided on each stage. The refrigerant flows in from the refrigerant pipe 97a on the upper rear side of the refrigeration evaporator 14a, flows downward on the right side of the refrigeration evaporator 14a, and flows into the rear of the first stage of the fin 98a. Then, it flows in order of 2nd stage back, 3rd stage back, 3rd stage front, 2nd stage front, 1st stage front, and flows out from the 1st stage right side. On the right side of the refrigeration evaporator 14a, a refrigeration gas-liquid separator 54a connected to the refrigerant pipe 97a is provided so that the liquid refrigerant and the gas refrigerant are separated. Further, a refrigeration evaporator temperature sensor 40a is attached to a refrigerant pipe at the upper rear of the refrigeration evaporator 14a by a sensor holder (not shown). The width W _Revp = 300 mm, the depth D _Revp = 60 mm, and the height H _Revp = 88 mm of the part (fin installation part) where the fins 98a where the main heat exchange is performed in the refrigeration evaporator 14a are installed. Occupied volume (refrigerator evaporator volume) V _Revp = 1.486L. Further, the fin pitch Pf _Revp = 3 mm. The surface area (air-side heat transfer area) A _{Revp in} contact with the air of the fin 98a and the refrigerant pipe 97a of the fin installation portion is 0.993 m ² .

FIG. 6B shows a refrigerating evaporator 14b, which is a fin-tube heat exchanger in which aluminum fins 98b are attached to an aluminum refrigerant pipe 97b. The refrigerant, which has been decompressed by the freezing capillary tube 53b (see FIG. 5) and has become low-temperature and low-pressure, flows through the refrigerant pipe 97b and flows back from the freezer compartment 7 and the vegetable compartment 6 from the lower front of the freezing evaporator 14b. (See FIG. 2 or FIG. 3) and heat exchange with the fins 98b and the surface of the refrigerant pipe 97b. The fin 98b is divided into five stages in the height direction of the refrigeration evaporator 14b, and two stages of refrigerant pipes 97b are provided at each stage. The refrigerant flows in from the refrigerant pipe 97b in front of the upper part of the refrigeration evaporator 14a and flows in front of the fifth stage of the fin 98a. After that, the 4th stage forward, 3rd stage forward, 2nd stage forward, 1st stage forward, 1st stage back, 2nd stage back, 3rd stage back, 4th stage back, 5th stage back , It flows out from the upper left behind the fifth stage. On the upper left side of the refrigeration evaporator 14b, a refrigeration gas-liquid separator 54b connected to the refrigerant pipe 97b is provided with a predetermined angle (15 degrees) with respect to the vertical line. Are to be separated. A refrigerating evaporator temperature sensor 40b is attached to a refrigerant pipe in front of the upper portion of the refrigerating evaporator 14a by a sensor holder (not shown). Width of the portion fin 98b of the main heat exchange is performed in the refrigeration evaporator 14b is installed (fin installation portion) is 1 stage to fourth stage _W Fevp 1 = 345mm, 5 stage _{W Fevp} 2 = 300 mm, depth D _Fevp = 60 mm, height H _evp1 = 118 mm of the first to fourth stages, and height H _evp1 = 30 mm of the fifth stage. The occupied volume of the fin installation portion determined from these (the volume of the evaporator for freezing) V _Fevp = 2.983 L, which is 3% or less of the rated internal volume 180 L of the freezer compartment 7. Thus, by setting the volume of the freezer evaporator to 3% or less of the rated internal volume of the freezer compartment 7, the rated internal volume of the freezer compartment 7 can be increased to 28% or more of the total rated internal volume. Further, the fin pitch Pf _Fevp = 5 mm, and the surface area (air side heat transfer area) A _Fevp = 1.146 m ² in contact with the air of the fin 98 _b and the refrigerant pipe _{97 b of} the fin installation portion.

The air side heat transfer areas per unit volume of the refrigeration evaporator 14a and the refrigeration evaporator 14b shown in FIG. 6 are A _Revp / V _Revp = 0.673 m ² / L and A _Fevp / V _Fevp = 0. 384m a ² / L, 0.25m ² / L or more, the following values 0.96 m ² / L. In general, frost grows on the air-side heat transfer surface of the evaporator. Therefore, if the air-side heat transfer area is increased with respect to the evaporator volume, the flow path is likely to be blocked when frost grows. For this reason, when the growth of frost is large, the heat exchange performance is likely to deteriorate, but when the growth of frost is small, the evaporator has a high heat exchange performance. On the other hand, if the air-side heat transfer area is reduced with respect to the evaporator volume, the flow path is not easily blocked by frost even if frost grows and it is easy to maintain heat exchange performance, but the air-side heat transfer area is reduced. When the frost growth is small, the heat exchange performance per unit volume is low. Therefore, in the refrigerator of this embodiment, the air-side heat transfer area per unit volume of the refrigeration evaporator 14a and the refrigeration evaporator 14b should be 0.25 m2 / L or more and 0.96 m2 / L or less. Therefore, the performance when the growth of frost is large and the performance when the growth of frost is small are made compatible.

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

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

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

When step S102 is not satisfied (No), it is subsequently determined whether the refrigeration operation end condition is satisfied (step S103). In the refrigerator of the present embodiment, the refrigerating compartment temperature _{T R} which is refrigerating chamber temperature sensor 41 for detecting the step S103 is satisfied when the refrigerating operation end temperature _{T Roff} (= 2.5 ℃) or less _{(T R} ≦ _{T Roff)} To do. When step S103 is not established (No), the process returns to the determination of step S102 again.

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

  If step S104 is established (if not established (No) (to be described later)), then the driving rotational speed of the compressor 24 is maintained, the three-way valve 52 is set to state 3 (fully closed mode), and the refrigeration evaporator 14a is filled. A refrigerant recovery operation for recovering the refrigerant to the heat dissipating means side is performed (step S105). At this time, the refrigeration fan 9a continues to drive and cools the refrigeration chamber 2 during the refrigerant recovery operation.

Subsequently, it is determined whether or not the refrigeration evaporator defrosting operation is performed (step S106). In the refrigerator of the present embodiment, when “temperature level 1” for maintaining the chilled room 35 provided at the lower part of the refrigerator room 2 at about 0 to 3 ° C. in the refrigerator temperature zone is selected, step S106 is performed. If established (Yes) and “temperature level 2” is selected to maintain the temperature in the refrigeration temperature range of about −3 to 0 ° C., step S106 is denied (No). When step S106 is established (Yes), the refrigeration fan 9a is set to speed 1 (900 min ⁻¹ ), the refrigeration evaporator defrosting operation is started (step S107), and when step S106 is not established (No), The refrigeration fan 9a is stopped (step S108).

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

Subsequently, it is determined whether or not the inside of the warehouse is heavily loaded (step S110). In the refrigerator of the present embodiment, the freezing compartment temperature T _F of the freezing compartment temperature sensor 42 is detected, a high load determination temperature T _{F_high} (= -10 ℃) or (T _F ≧ T _{F_high),} or, the refrigerating compartment temperature sensor 41 Step S110 is established when the refrigeration room temperature T _R detected by is _{equal to} or higher than the high load determination temperature T _{R_high} (= 10 ° C.) (T _R ≧ T _{R_high} ) (determination similar to Step S102). The control when step S110 is established will be described later.
When step S110 is not satisfied (No), it is next determined whether or not the vegetable room cooling end condition is satisfied (step S111). In the refrigerator of this embodiment, vegetable compartment temperature T _V of vegetable compartment temperature sensor 43 is detected, step S111 in the case of vegetable compartment cooling end temperature T _{V_off} (= 4 ℃) or less (T _V ≦ T _{V_off)} is satisfied . When Step S111 is established (Yes), the vegetable compartment damper 19 is closed, the frozen vegetable operation is finished, and the operation is shifted to the freezing operation for cooling the freezer compartment 7.

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

When step S113 is not satisfied (No), it is subsequently determined whether the freezing operation end condition is satisfied (step S115). In the refrigerator of the present embodiment, when the vegetable compartment damper 19 is closed and the freezer compartment temperature T _F is equal to or lower than the freezing operation end temperature T _{F_off} (= −22.5 ° C.) (T _F ≧ T _{F_off} ), step S115. Is established. When step S115 is not established (No), the process returns to the determination of step S110.

If step S115 is satisfied, it is next determined whether the refrigeration operation start condition is satisfied (step S116). In the refrigerator of the present embodiment, in the refrigerator of the present embodiment, the refrigerating compartment temperature T _R which is refrigerating chamber temperature sensor 41 for detecting the refrigeration operation start temperature T _{R_on (=} 5.5 ℃) or (T _R ≧ T _{R_on)} In this case, step S116 is established.

  If step S116 is satisfied (if not satisfied (No) (to be described later)), the drive rotational speed of the compressor 24 is maintained, the three-way valve 52 is set to state 3 (fully closed mode), and the refrigeration evaporator 14b A refrigerant recovery operation for recovering the refrigerant to the heat radiating means side is performed (step S117). At this time, the refrigeration fan 9b continues to drive and cools the freezer compartment 7 even during the refrigerant recovery operation.

When step S104 is not established (No), it is subsequently determined whether or not the refrigeration evaporator defrosting operation is performed (step S201). In the refrigerator of the present embodiment, when “temperature level 1” for maintaining the chilled room 35 provided at the lower part of the refrigerator room 2 at about 0 to 3 ° C. in the refrigerator temperature zone is selected, step S106 is performed. If “temperature level 2” that is established (Yes) and is maintained at about −3 to 0 ° C. of the refrigeration temperature zone is selected, step S106 is not established (No) (the same determination as step S106) ). If step S201 is established (Yes), the refrigeration fan 9a is set to speed 1 (900 min ⁻¹ ) and the refrigeration evaporator defrosting operation is started (step S202). If step S106 is not established (No), The refrigeration 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 refrigeration fan 9b is stopped (step S118). When step S116 is not established (No), the three-way valve 52 is set to state 3 (fully closed mode), the compressor 24 is stopped, and the refrigeration fan 9b is stopped (step S118).

Subsequently, it is determined whether or not the inside of the warehouse is heavily loaded (step S119). In the refrigerator of the present embodiment, the freezing compartment temperature T _F of the freezing compartment temperature sensor 42 is detected, a high load determination temperature T _{F_high} (= -10 ℃) or (T _F ≧ T _{F_high),} or, the refrigerating compartment temperature sensor 41 Step S119 is established when the refrigeration room temperature T _R detected by is higher than the high load determination temperature T _{R_high} (= 10 ° C.) (T _R ≧ T _{R_high} ) (the same determination as in Steps S102 and 110). The control when step S119 is established will be described later.
When step S119 is not satisfied (No), it is then determined whether the refrigeration evaporator defrosting operation end condition is satisfied (step S120). The refrigeration evaporator defrosting operation end condition is _satisfied when the refrigeration evaporator temperature T _{R_evp} is _equal to or higher than the refrigeration evaporator defrosting operation end temperature T _{RD_off} (= 2 ° C.) ( _{TR_evp} ≧ T _{RD_off} ). Determination similar to S113). When step S120 is established (Yes), the refrigeration fan 9a is stopped (step S121), and the “end of refrigeration evaporator defrosting operation” is completed.

When 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 the present embodiment, step S122 is established when the freezer temperature _TF detected by the freezer temperature sensor 42 is _{equal to} or higher than the frozen vegetable operation start temperature _{TF_on} (= −18 ° C.) ( _TF ≧ _{TF_on} ). (Same determination as in step S104). When step S122 is established (Yes), it is next determined whether or not the refrigerant recovery operation is necessary (step S123). In the refrigerator of the present embodiment, step S123 is established when the operation immediately before the stop of the compressor 24 in step S118 is the refrigeration operation. When step S123 is established (Yes), the three-way valve 52 is set to the state 3 (fully closed mode), the compressor 24 is driven at the rotational speed in the immediately preceding refrigeration operation, and the refrigerant in the refrigeration evaporator 14a is dissipated. A refrigerant recovery operation for recovering to the side is performed (step S124), and a 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).

When step S122 is not satisfied (No), it is subsequently determined whether the refrigeration operation start condition is satisfied (step S125). In the refrigerator of the present embodiment, the refrigerating compartment temperature _{T R} which is refrigerating chamber temperature sensor 41 for detecting the step S116 is satisfied when the refrigerating operation start temperature _{T R_on} (= 5.5 ℃) or (T _R ≧ T _{R_on)} (Same determination as in step S116).

  When step S125 is established, it is next determined whether or not the refrigerant recovery operation needs to be performed (step S126). In the refrigerator of the present embodiment, step S126 is established when the operation immediately before the stop of the compressor 24 in step S118 is the refrigeration 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 rotational speed in the immediately preceding refrigeration operation, and the refrigerant in the refrigeration evaporator 14b is dissipated. A refrigerant recovery operation for recovering to the side is performed (step S127), and a refrigeration operation is started (step S101). When step S126 is not established (No), the refrigeration operation is started without performing the refrigerant recovery operation (step S101).

In the above description, the refrigeration operation start temperature T _{R_on} (= 5.5 ° C.), the refrigeration operation end temperature T _{R_off} (= 2.5 ° C.) _{, the} frozen vegetable operation start temperature T _{F_on} (= −18 ° C.), the freezing operation The end temperature T _{F_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”. Varies according to the maintenance temperature level.

  Next, control when the inside of the refrigerator 1 is heavily loaded will be described with reference to FIG. The control shown in FIG. 8 is shifted to the case where it is determined in steps S102, S110, and S119 in FIG. 7 that the inside of the refrigerator 1 has a high load (the determination in each step is Yes). If it is determined that the inside of the refrigerator has a high load, then it is determined whether the refrigerator compartment 2 has a high load (step S301) or whether the freezer compartment 7 has a high load (step S302). If the refrigerator compartment 2 is heavily loaded and the freezer compartment 7 is not heavily loaded, step S301 is No, and it is then determined whether the refrigerant recovery operation is necessary (step S501).

In the refrigerator of the present embodiment, step S501 is established when the operation at the time when any of steps S102, S110, and S119 in FIG. 7 is established is the refrigeration 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 rotational speed in the immediately preceding refrigeration operation, and the refrigerant in the refrigeration evaporator 14a is dissipated. Next, a refrigerant recovery operation is performed (step S502), and then “high load mode frozen vegetable operation” is selected (step S503). When step S501 is not established (No), “high load mode frozen vegetable / freezing operation” is selected without performing the refrigerant recovery operation (step S503). In the refrigerator of the present embodiment, when “high load mode frozen vegetable / freezing operation” is selected, the compressor 24 has a speed of 4 (3600 min ⁻¹ ) as the rotation speed when the frozen vegetable operation or the freezing operation is performed. The refrigeration fan 9b is set at a speed of 2 (2000 min ⁻¹ ). Note that the rotational speeds of the compressor 24 and the refrigeration fan 9a when the refrigeration operation and the refrigeration evaporator defrosting operation are performed are the same as those in the normal operation mode.

  If the freezer compartment 7 has a high load (Yes at Step S301) and the refrigerator compartment 2 is not at a high load, Step S302 is No, and then it is determined whether or not the refrigerant recovery operation is necessary (Step S401).

In the refrigerator of the present embodiment, step S401 is established when the operation at the time when any of steps S102, S110, and S119 in FIG. 7 is established is the frozen vegetable operation or the freezing 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 rotational speed in the immediately preceding frozen vegetable operation or freezing operation, and the inside of the freezing evaporator 14b is set. A refrigerant recovery operation for recovering the refrigerant to the heat radiating means side is performed (step S402), and then “high load mode refrigeration operation” is selected (step S403). When step S401 is not established (No), the “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 compressor 24 is set to a rotational speed of 3 (2500 min ⁻¹ ) and the refrigeration fan 9 a is set to a speed of 3 (2000 min ⁻¹ ). The The rotation speeds of the compressor 24, the refrigeration fan 9a, and the refrigeration fan 9b when the frozen vegetable operation, the refrigeration operation, and the refrigeration evaporator defrost operation are performed are selected to be the same as the normal operation mode. .

When the freezer compartment 7 and the refrigerator compartment 2 are both heavily loaded (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 the present embodiment, step S303 is established when the operation at the time when any of steps S102, S110, and S119 in FIG. 7 is established is the refrigeration operation. When step S303 is established (Yes), the three-way valve 52 is set to state 3 (fully closed mode), the compressor 24 is driven at the rotational speed in the immediately preceding refrigeration operation, and the refrigerant in the refrigeration evaporator 14a is dissipated. The refrigerant recovery operation for recovering to the side is performed (step S304), and then the “overload mode” is selected (step S305). In the refrigerator of the present embodiment, when “overload mode” is selected, the compressor 24 has a speed 3 (2500 min ⁻¹ ) and the refrigeration fan 9 a has a speed 3 ( 2000 min ^-1), as the rotational speed when the frozen vegetables operation or freezing operation is carried out, the compressor 24 speed 4 (3600 min ^-1), freezing fan 9b is set to speed 2 (2000min ^-1). The rotation speed of the refrigeration fan 9a when the refrigeration evaporator defrosting operation is performed is selected to be the same as that in the normal operation mode.

When “overload mode” is selected in step S305, the three-way valve 52 is set to state 2 (refrigeration mode), the compressor 24 is set to speed 4 (3600 min ⁻¹ ), and the refrigeration fan 9b is set to speed 2 (2000 min ⁻¹ ). And the vegetable compartment damper 19 is opened to start the frozen vegetable operation (step S306). Subsequently, the refrigeration fan 9a is driven at a speed of 1 (900 min ^-1 ) to perform the refrigeration evaporator defrosting operation. To 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, vegetable compartment temperature T _V of vegetable compartment temperature sensor 43 is detected, step S307 in the case of vegetable compartment cooling end temperature T _{V_off} (= 6 ℃) or less (T _V ≦ T _{V_off)} is satisfied . When Step S308 is established (Yes), the vegetable compartment damper 19 is closed, the frozen vegetable operation is finished, and the operation proceeds to the freezing operation for cooling the freezer compartment 7 (Step S309).

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

When 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 the present embodiment, when the vegetable compartment damper 19 is closed and the freezer compartment temperature T _F is equal to or lower than the freezing operation end temperature T _{F_off} (= −22.5 ° C.) (T _F ≧ T _{F_off} ), or Step S312 is established when the duration of the frozen vegetable operation or the freezing operation reaches a predetermined value (42.5 minutes). If step S312 is not satisfied (No), the process returns to the determination of step S308.

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

Subsequently, a determination is made as to whether to shift to the normal operation mode (step S314). In the refrigerator of the present embodiment, the refrigerating compartment temperature sensor 41 detects the refrigerating compartment temperature _{T R} refrigeration operation start temperature _{T R_on} (= 5.5 ℃) or less (T _R ≦ T _{_on),} the freezing compartment temperature sensor 42 is detected If the freezer compartment temperature T _F is simultaneously satisfied with the frozen vegetable operation start temperature T _{F — on} (= −18 ° C.) or less (T _R ≦ T _{F — on} ), step S314 is established (Yes), and the normal operation mode is set. Return (step S101 in FIG. 7)
When step S314 is not established (No), the refrigeration operation is subsequently performed (step S315). Refrigerating operation, the three-way valve 52 is in the state 1 (refrigerating mode), the compressor 24 speed 3 driven by (2500min ^-1), drives the refrigerating fan 9a at a speed 3 (2000 min ^-1), freezing fan 9b Is started and the vegetable compartment damper 19 is closed.

Next, it is determined whether the freezer compartment 7 has a high load (step S316). In the refrigerator of the present embodiment, step S316 is established when the freezer compartment temperature T _F detected by the freezer compartment temperature sensor 42 is _{equal to} or higher than the high load determination temperature T _{F_high} (= −10 ° C.) ( _TF ≧ _{TF_high} ). (Yes). When step S316 is established (Yes), the refrigerant recovery operation is performed (step S304), and the process shifts to the overload mode (step S305). Note that the determination in step S316 is skipped until a predetermined time (5 minutes) has elapsed since the start of the refrigeration operation.

When step S316 is not satisfied (No), the process proceeds to determination (step S317) whether the refrigeration operation end condition is satisfied. In the refrigerator of the present embodiment, the case of the refrigerating compartment temperature T _R is refrigerating operation end temperature T _{R_off} (= 2.5 ℃) or less (T _R ≦ T _{R_off),} or, the duration of refrigerating operation in overload mode predetermined Step S317 is established when the value (20.5 minutes) is reached. If step S317 is not satisfied (No), the process returns to the determination in step S316 again. If step S317 is satisfied (Yes), the three-way valve 52 is set to state 3 (fully closed mode), and the refrigeration evaporator 14a is set. A refrigerant recovery operation for recovering the refrigerant to the heat radiating means side is performed (step S318). At this time, the refrigeration fan 9a continues to drive.

Subsequently, a determination is made as to whether to shift to the normal operation mode (step S319). In the refrigerator of the present embodiment, the refrigerating compartment temperature sensor 41 detects the refrigerating compartment temperature _{T R} refrigeration operation start temperature _{T R_on} (= 5.5 ℃) or less (T _R ≦ T _{R_on),} the freezing compartment temperature sensor 42 is detected If the freezer compartment temperature T _F is simultaneously satisfied with the frozen vegetable operation start temperature T _{F — on} (= −18 ° C.) or less (T _R ≦ T _{F — on} ), step S318 is established (Yes), and the normal operation mode is set. Return (step S109 in FIG. 7).

  If “high load mode refrigeration operation” is selected in step S403, the process proceeds to step S315 to start refrigeration operation. If “high load mode frozen vegetable / frozen operation” is selected in step S503, , The process proceeds to step S306, and the frozen vegetable operation is started. Thereafter, the control is performed according to the control flow described above.

In the refrigerator of the present embodiment, the refrigerant recovery operation in step S105 and step S301 is performed when the compressor 24 is driven at a speed 1 (800 min ⁻¹ ) and the refrigeration fan 9a is driven at a speed 2 (1500 min ⁻¹ ). For 2 minutes, the compressor 24 is driven at a speed of 3 (2500 min ^-1 ) and the refrigeration fan 9a is driven at a speed of 3 (2000 min ^-1 ) for 1.5 minutes. The refrigerant recovery operation in steps S112 and S302 is performed for 2.5 minutes when the compressor 24 is driven at speed 2 (1400 min ^-1 ) and the refrigeration fan 9b is driven at speed 1 (1200 min ^-1 ). When the machine 24 is driven at a speed of 4 (1400 min ⁻¹ ) and the refrigeration fan 9 b is driven at a speed of 2 (2000 min ⁻¹ ), the operation is performed for 1.5 minutes.

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

The amount of circulating air in the freezer compartment 7 at the rotational 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 room damper 19 is closed (during freezing operation), the flow rate is 0.6 m ³ / min, and the amount of circulating air in the vegetable room 6 when the vegetable room damper 19 is opened (during frozen vegetable operation) is 0. 07 m ³ / min.

The circulating air volume in the refrigerator compartment 2 at the rotational speed (speed 3 = 2000 min ⁻¹ ) of the refrigeration fan 9a during the refrigeration operation in the high load mode or the overload mode is 0.52 m ³ / min. Further, the circulating air volume in the freezer compartment 7 at the rotational 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 freezing operation), and the circulating air volume in the vegetable compartment 6 when the vegetable compartment damper 19 is opened (during frozen vegetable operation) is 0.12 m ³ / min.

  FIG. 9 is a time chart showing a state where the refrigerator according to the present embodiment is installed in an environment of 32 ° C. and a relative humidity of 70% and a 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 chilled room 35 is set to “temperature level 1”.

Elapsed time t ₀ is the start of refrigerating operation for cooling the refrigerating compartment 2 (step S101 in FIG. 7) is the elapsed time. In the refrigeration operation in the normal operation mode, the three-way valve 52 is controlled to the state 1 (refrigeration mode), the compressor 24 is driven at a speed 1 (800 min ⁻¹ ), and the refrigerant is supplied to the refrigeration evaporator 14a. The temperature of the refrigeration evaporator 14a is decreasing. In this state, the refrigeration fan 9a is driven at a speed of 2 (1500 min ⁻¹ ), so that the low temperature air passing through the refrigeration evaporator 14a is supplied from the refrigeration chamber discharge port 11a (see FIG. 2). The refrigeration chamber 2 is cooled and the temperature is lowered.

Here, the time average temperature of the refrigeration evaporator 14a during the refrigeration operation is −6 ° C., which is higher than the time average temperature -24 ° C. of the refrigeration evaporator 14b during the refrigeration operation described later. Generally, the higher the evaporator temperature (evaporation temperature), the higher the coefficient of performance of the refrigeration cycle (the ratio of the endothermic amount to the input of the compressor 24), and the higher the energy saving performance. In order to maintain the freezing temperature in the freezer compartment 7 at the freezing temperature, the temperature of the freezing evaporator 14b needs to be lowered. However, since the refrigerating room 2 only needs to be maintained at the refrigerating temperature, the temperature of the refrigerating evaporator 14a should be increased. In addition, the rotational speed of the refrigeration fan 9a and the compressor 24 is controlled to improve the energy saving performance. Elapsed time by the refrigerating compartment temperature T _R of the refrigerating compartment temperature sensor 41 at _{t 1} is detected is decreased to refrigerating operation end temperature _{T R_off,} steps S104, S105 (FIG. 7 are switched to the refrigerant recovery run from refrigerating operation ). In the refrigerant recovery operation, the three-way valve 52 is controlled to state 3 (fully closed mode), the compressor 24 is driven at speed 1 (800 min ⁻¹ ), and the refrigeration fan 9a is driven at speed 2 (1500 min ⁻¹ ). The refrigerant in the evaporator 14a is recovered for 2 minutes (ΔT _A1 = 2 min). Thereby, the cooling efficiency fall by the refrigerant | coolant shortage by the following frozen vegetable driving | operation and freezing driving | operation can be suppressed. At this time, when the refrigeration fan 9a is driven, the residual refrigerant in the refrigeration evaporator 14a is utilized for cooling the refrigeration chamber 2, and the refrigeration evaporator is heated by the air in the refrigeration chamber 2. The pressure drop in 14a is alleviated. As a result, an increase in the specific volume of the suction refrigerant of the compressor 24 is suppressed, and a large amount of refrigerant can be recovered in a relatively short time, thereby improving the cooling efficiency.

When the refrigerant recovery operation ends (elapsed time t ₂ ), it is determined whether or not the refrigeration evaporator defrosting operation is performed. Here, since the setting of the chilled room 35 is “temperature level 1”, the refrigeration fan 9a is driven at a speed of 1 (900 min ⁻¹ ), and the refrigeration evaporator defrosting operation is performed (steps S106 and S107 in FIG. 7). As a result, the temperature of the refrigeration evaporator 14a rises, and the temperature rise of the refrigeration chamber 2 is mitigated by the cooling effect of frost and the cold storage heat of the refrigeration evaporator 14a. The freezing compartment temperature T _F of the freezing compartment temperature sensor 42 detects the elapsed time t ₂ is, frozen vegetables driving frozen vegetables operation since the start has a temperature T _{F_on} above is started, the vegetable compartment vegetable compartment 6 is cooled temperature _{T V} is decreased. In the frozen vegetable operation, the three-way valve 52 is controlled to the state 2 (freezing mode), the compressor 24 is driven at the speed 2 (1400 min ⁻¹ ), and the refrigerant is supplied to the freezing evaporator 14b. 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 (1200 min ⁻¹ ), so that the air that has passed through the freezing evaporator 14b and has been cooled to the freezer compartment 7 and the vegetable Chamber 6 is cooled.

By vegetable compartment temperature T _V of vegetable compartment temperature sensor 43 is detected reaches the vegetable compartment cooling end temperature T _{V_off} by the elapsed time t _3, the vegetable compartment damper 19 is closed, and moves to the freezing operation (Fig. 7 Steps S111 and S112).

Then as the temperature T _REVP of refrigerating evaporator 14a for refrigerating evaporator temperature sensor 40a detects the elapsed time t ₄ reaches the refrigerating evaporator defrosting operation end temperature T _{RD_off,} the refrigeration fan 9a stop Thus, the refrigeration evaporator defrosting operation is completed (steps S113 and S114 in FIG. 7).

Freezing compartment temperature T _F of the freezing compartment temperature sensor 42 detects the elapsed time t ₅ reaches the freezing operation completion temperature T _{F_off,} and, since the vegetable compartment damper 19 is closed, the freezing operation is completed (Step S115 in FIG. 7). Since this time the refrigerating compartment temperature T _R which is refrigerating chamber temperature sensor 41 detects is reached over the refrigerating operation start temperature T _{R_on,} refrigerating operation start condition is satisfied (step S116 in FIG. 7), the refrigerant recovering operation is row (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 speed 2 (1400 min ⁻¹ ), and the refrigeration fan 9 b is driven at speed 1 (1200 min ⁻¹ ). The refrigerant in the evaporator 14b is recovered for 1.5 minutes (Δt _B1 = 1.5 min). Thereby, the cooling efficiency fall by the refrigerant | coolant shortage by the following refrigeration operation can be suppressed. At this time, by driving the refrigeration fan 9b, the refrigerant remaining in the refrigeration evaporator 14b is used for cooling the refrigeration chamber 7, and the inside of the refrigeration evaporator 14b is heated by the air in the refrigeration chamber 7. This reduces the pressure drop. As a result, an increase in the specific volume of the suction refrigerant in the compressor 24 is suppressed, and a large amount of refrigerant can be recovered in a relatively short time, thereby improving the cooling efficiency.

The operation in which the freezer compartment 7 is cooled includes the frozen vegetable operation (t2 to t3), the freezing operation (t3 to t5), and the refrigerant recovery operation (t5 to t6). The refrigeration 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 refrigeration chamber discharge air temperature during the refrigeration operation, the refrigerant recovery operation, and the refrigeration evaporator defrosting operation in which the refrigeration fan 9a is in operation is −1.5 ° C. The temperature is higher than the arithmetic average value (−8 ° C.) of the freezer compartment maintenance temperature T _{F — keep} (−20 ° C.) and the refrigerator compartment maintenance temperature T _{R — keep} (4 ° C.).

Again from the elapsed time t ₆ to the refrigerant recovery run is completed, refrigerating operation is started (step S101 in FIG. 7), are repeated periodically in the above operation thereafter, the refrigerating compartment 2 to about 4 ° C., the freezing compartment 7 about -20 ℃, vegetable room is maintained at about 7 ℃.

  FIG. 10 is a time chart showing an operation state when the refrigerator according to this example is installed in an environment of 32 ° C. and a load cooling test defined in JIS C9801-3: 2015 is performed. In refrigerators, it is important not only to open and close the doors, but also to cool them stably, as well as to cool well when a practical load such as food is applied. . JISC9801-3: 2015 defines a “load cooling test” that assumes a practical load (hereinafter referred to as “practical load”) after fully considering the usage of general refrigerators. As a practical load, water of the same temperature as the outside air is used, 12g per 1L rated internal volume of the refrigerated temperature zone (refrigerated room and vegetable room), 4g per 1L rated internal volume of the refrigeration zone (freezer compartment) It is stipulated that the water is put into the refrigerator compartment and the freezer compartment, respectively.

  At the elapsed time t0 in the state where the refrigeration operation (see FIG. 9) in the stable cooling operation is performed, the door 2a of the refrigerator compartment 2 is opened for one minute according to the procedure defined in JIS C9801-3: 2015, and the refrigerator compartment is kept. As a practical load of (refrigeration room 2 and vegetable room 6), 5064 g of water at 32 ° C. (a load corresponding to a rated internal volume of 422 L of the refrigeration temperature zone (refrigeration room 2 and vegetable room 6)) is sealed in a 500 mL plastic bottle and refrigerated. It is installed at a predetermined position in the chamber 2. Subsequently, the door 5a of the freezer compartment 7 (lower freezer compartment 5) is opened for 1 minute, and 720 g of water at 32 ° C. (the load corresponding to the rated internal volume of 180 L of the freezer temperature zone (freezer compartment 7)) is supplied to the freezer compartment 7 ( It is installed at a predetermined position in the lower freezer compartment 5).

Thus, first, the refrigerating compartment temperature T _R is increased, due to exceeding the refrigerating chamber high load determination temperature T _{R_high,} refrigerator compartment 2 is determined to be a high load (step S110 in FIG. 7). At this point, although the refrigerating compartment temperature T _R is determined that a high load beyond the refrigerating compartment high load determination temperature T _{R_high,} freezing compartment temperature T _F does not reach the high load determination temperature T _{F_high.} Therefore, although step S301 in FIG. 8 is satisfied (Yes), step S302 is not satisfied (No), and it is next determined whether or not the refrigerant recovery operation is necessary (step S401 in FIG. 8). Since the operation mode at the time of the determination in step S110 is the refrigeration operation, it is determined here that the refrigerant recovery operation is necessary (step 401 in FIG. 8 is Yes), the compressor 24 is at speed 2 (1400 min ⁻¹ ), and the refrigeration operation is performed. Refrigerant recovery operation is performed in which the refrigerant in the refrigeration 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 refrigeration fan 9b, the freezer compartment 7 is cooled by the endothermic action of the residual refrigerant in the refrigeration evaporator 14b (freezer compartment cooling operation (F)).

At the elapsed time t ₀ ′, the refrigerant recovery operation ends, and then the three-way valve 52 is controlled to the state 1 (refrigeration mode), the compressor 24 is at speed 3 (2500 min ⁻¹ ), and the refrigeration fan 9 a is at speed 3 ( The refrigeration fan 9b is driven at 2000 min ⁻¹ ), and the high load mode refrigeration operation in which the refrigeration fan 9b is stopped is performed (steps S403 and S315 in FIG. 8).

Although the freezer temperature _TF rises and exceeds the high load judgment temperature _{TF_high} due to the practical load put into the freezer compartment 7 (lower freezer compartment 5), it is shown in FIG. 8 until 5 minutes have passed since the transition to the refrigeration operation. Since step S316 is not established, the high load mode refrigeration operation is continued.

By 5 minutes elapsed time t ₁ is the lowest elapsed time after the refrigerating operation shift condition established has elapsed, satisfied step S316 shown in FIG. 8 (Yes), through the refrigerant recovering operation (steps S304 of FIG. 8) , Transition to the overload mode 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 the speed 3 (2500 min ⁻¹ ), and the refrigeration fan 9 a is driven at the speed 3 (2000 min ⁻¹ ). Thus, the refrigerant in the refrigeration evaporator 14a is recovered for 1.5 minutes (Δt _B2 = 1.5 min). This refrigerant recovery operation is completed at the elapsed time t ₁ ′. By driving the refrigeration fan 9a during the refrigerant recovery operation, the refrigeration chamber 2 is cooled by the endothermic action of the residual refrigerant in the refrigeration evaporator 14a.

From the elapsed time t ₀ ′ to the elapsed time t ₁ ′, an operation state (cooling room cooling operation (R)) in which the refrigerator compartment is cooled is entered.

From the elapsed time t ₁ becomes overloaded mode, frozen vegetables operation is started to cool the freezing chamber 7 (step S306 in FIG. 8). Frozen vegetables operation overload mode, three-way valve is controlled to a state 2 (freezing mode), the compressor 24 speed 4 (3600 min ^-1), freezing fan 9b is driven at a speed 2 (2000 min ^-1), This is performed with the vegetable room damper 19 opened. By this operation, the freezer compartment 7 and the vegetable compartment 6 are cooled. At this time, the refrigeration fan 9a is driven at a speed of 1 (900 min ⁻¹ ), so that the refrigeration evaporator defrosting operation is performed (step S307 in FIG. 8). In the elapsed time t _2, as the temperature T _REVP of refrigerating evaporator 14a for refrigerating evaporator temperature sensor 40a detects reaches the refrigerating evaporator defrosting operation end temperature T _{RD_off,} refrigerating fan 9a is stopped The refrigeration evaporator defrosting operation has been completed (steps S310 and S311 in FIG. 8).

In the elapsed time t _3, the vegetable compartment temperature T _V of vegetable compartment temperature sensor 43 is detected, vegetable compartment damper 19 is closed by reaching the following vegetable compartment cooling end temperature _{T V_off (T V ≦ T V_off} ) refrigerating operation (Steps S308 and S309 in FIG. 8).

In the elapsed time t _4, since the elapsed time from the frozen vegetables operation start overload mode has reached a predetermined value (42.5Min), frozen vegetables / freezing operation end condition is satisfied (step S312 in FIG. 8), the freezing operation Has been completed and the operation has shifted to the refrigerant recovery operation. Refrigerant recovery operation at this time, the three-way valve 52 is controlled to the state 3 (fully closed mode), the compressor 24 speed 4 (3600 min ^-1), freezing fan 9b is driven at a speed 2 (2000 min ^-1) Thus, the refrigerant in the freezing evaporator 14b is recovered for 1.5 minutes (Δt _C2 = 1.5 min). This refrigerant recovery operation is completed at the elapsed time t ₄ ′. By driving the refrigeration fan 9b during the refrigerant recovery operation, the freezer compartment 7 is cooled by the endothermic action of the residual refrigerant in the refrigeration evaporator 14b. From the above, the elapsed times t ₁ ′ to t ₄ ′ are operations in which the freezer compartment 7 is cooled (freezer compartment cooling operation (F)).

Subsequently, the shift to the normal operation mode is determined (step S312 in FIG. 8), the refrigerating compartment temperature T _R in the elapsed time t _{4 ',} the freezing compartment temperature T _F together refrigerating operation start temperature T _{R_on} and frozen vegetables Since it is higher than the operation start temperature _{TF_on} , it is not established, and the operation shifts to the overload mode refrigeration operation (step S315 in FIG. 8). As a result, the three-way valve 52 is controlled to the state 1 (refrigeration mode), the compressor 24 is driven at speed 3 (2500 min ⁻¹ ), the refrigeration fan 9 a is driven at speed 3 (2000 min ⁻¹ ), and the freezing fan 9 b is The refrigeration operation in the overload mode that is in a stopped state is performed (steps S315 and S315 in FIG. 8).

By the elapsed time t duration of refrigerating operation overload mode in ₅ has reached the predetermined value (20.5min), (step S317 of FIG. 8) refrigerating operation end condition is satisfied, the process proceeds to the refrigerant recovery run (Step S318 in FIG. 8). In this refrigerant recovery operation, the three-way valve 52 is controlled to the state 3 (fully closed mode), the compressor 24 is driven at speed 3 (2500 min ⁻¹ ), and the refrigeration fan 9 a is driven at speed 3 (2000 min ⁻¹ ). Thus, the refrigerant in the refrigeration evaporator 14a is recovered for 1.5 minutes. This refrigerant recovery operation is completed at the elapsed time t ₅ ′ (control similar to the refrigerant recovery operation performed at the elapsed time t _{1 to} t ₁ ′). From the above, the elapsed time t ₄ ′ to t ₅ ′ is an operation (cooling room cooling operation (R)) in which the refrigerator compartment 2 is cooled.

Thereafter refrigerating compartment 2 by the same control as the elapsed time t _{1 '~t 5',} the freezing compartment 7, the cooling of the vegetable compartment 6 is performed. Specifically, the elapsed time _{t 5 ~t 8, t 9 ~t} 12, t 13 ~t 17 refrigeration compartment cooling operation, the elapsed time _{t 8 ~t 9, t 12 ~t} 13, t 17 ~t 19 is Refrigerated room cooling operation. _{Also, t 5 ~t 6, t 9} ~t 10, t 13 refrigerating evaporator defrosting operation to _{~t 14} is performed.

Whether practical load is sufficiently cooled, the refrigerating compartment temperature T _R is the refrigerating compartment maintained temperature T _Rkeep + 1 ℃ or less, depending on whether or not the freezing compartment temperature T _F is cooled to below freezing compartment maintained temperature T _Fkeep + 1 ℃ Can be judged. The refrigerator compartment maintenance temperature T _Rkeep + 1 ° C. or less and the freezer compartment maintenance temperature T _Fkeep + 1 ° C. or less may not be satisfied simultaneously. In the present specification, a period from when a load is applied to the refrigerator compartment 2 to a state where the practical loads input to the refrigerator compartment 2 and the freezer compartment 7 can be regarded as sufficiently cooled is referred to as a load cooling section. In the refrigerator of this embodiment, the freezer compartment temperature T _F reaches the freezer compartment maintenance temperature T _{F_keep} + 1 ° C. at t ₁₆ shown in FIG. 10, and the refrigerating compartment temperature T _R reaches the refrigerator compartment maintenance temperature T _{R_keep} + 1 ° C. at t _18. Thus, the load cooling section is from t ₀ when the practical load is input to the refrigerator compartment 2 to t ₁₈ where the practical loads of the refrigerator compartment 2 and the freezer compartment 7 can be considered sufficiently cooled.

Here, the refrigerator of the present embodiment, the cooling state of the refrigerator compartment 2 and the freezer compartment has been practically load application 7 includes a refrigerating compartment temperature T _R which is refrigerating chamber temperature sensor 41 for detecting, detected freezer compartment temperature sensor 42 The freezer compartment 2 and the freezer compartment 7 are represented by the method defined in JIS C9801-1: 2015 in order to more reliably discriminate 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.
In the elapsed time _{t 19,} (step S319 of FIG. 8) determines whether to shift to the normal operation mode is performed, the refrigerating compartment temperature _{T R} refrigeration operation start temperature _{T R_on} below (T _R ≦ T _{R_on),} freezing chamber since the temperature _{T F} meets frozen vegetables operation start temperature _{T F_on} below _{(T R} ≦ T _{F_on)} simultaneously, by the overload mode ends (step S319 of FIG. 8 _{Yes), t 19} after the normal operation mode Cooling is taking place.

In this way, by putting a practical load on the refrigerator compartment 2 and the freezer compartment 7 at t ₀ , both the refrigerator compartment 2 and the freezer compartment 7 are in a high load state, so that the overload mode is entered, and the refrigerator compartment 2 is cooled. and it is the driver (the refrigerating compartment cooling operation), the operation of the freezing compartment 7 is cooled (freezer compartment cooling operation) is performed alternately, practical load t ₁₈ is sufficiently cooled, and returned to the normal mode.

Until the practical load is sufficiently cooled at t ₁₇₁₈ , the freezer compartment temperature T _F is T _F1 (= −7 ° C.) at t ₁ , T _F2 (= −11 ° C.) at t ₅ ′, and T _F at t ₉ . The maximum value of T _F4 (= −16.5 ° C.) is taken at _F3 (= −14 ° C.) and t ₁₃ , but each maximum value gradually decreases (T _F1 > T _F2 > T _F3 > T _F4 ). .

In the operation of the load cooling section (t _{0 to} t ₁₈ ), the refrigerator compartment cooling operation (t ₀ ′ to t ₁ ′, t ₄ ′ to t ₅ ′, t _{8 to} t ₉ , _{t 12 ~t 13, t 17 ~t} 18 time average temperature _{T Revp_ave} the refrigerating evaporator 14a in) is -6.0 ° C., freezing compartment cooling operation the freezing compartment 7 is cooled (t ₀ ~t ₀ ', t ₁ ′ to t ₄ ′, t ₅ ′ to t ₈ , t _{9 to} t ₁₂ , t _{13 to} t ₁₇ ), the time average temperature T _{Fevp_ave} of the refrigeration evaporator 14 b is −23.0 ° C., and T _{Revp_ave} > T _{Fevp_ave} .

Furthermore, from the point of introducing the load, _{t 0} in the operation in the normal in operation until the operation mode is resumed _(t 0 _{~t 17),} the time ratio as an refrigerating compartment cooling operation _(t 0 _{~t 17 '~t 1 ', t 4' ~t 5} ', t 8 ~t 9, t 12 ~t 13, t 16 time rate of _{~t 17) R R = 34%} , the freezing compartment vegetable compartment cooling the freezing compartment 7 is cooled Time ratio for operation or freezer cooling operation (t _{0 to} t ₀ ′, t ₁ ′ to t ₄ ′, t ₅ ′ to t ₈ , t ₉ to t ₁₂ , t ₁₃ to t _{0 to} t ₁₇ t ₁₆ time ratio) R _F = 66%, and the ratio R _F / R _R = 1.94 of the two. On the other hand, the outside air temperature T _out (= 32 ° C.), the air side heat transfer area A _Revp (= 0.993 m ² ) of the refrigeration evaporator 14a, and the time average temperature during the refrigeration chamber cooling operation of the refrigeration evaporator 14a are T _{Revp_ave} (= −6.0 ° C.), refrigeration room maintenance temperature is T _{R_keep} (= 4.0 ° C.), air side heat transfer area A _Fevp (= 1.146 m ² ) of refrigeration evaporator 14b, refrigeration evaporator 14b b freezing room cooling operation time average temperature T _{Fevp_ave} (= -23.0 ℃, freezing room maintenance temperature _{TF_keep} (= -20 ℃), refrigeration temperature zone (refrigeration room and vegetable room) rated content Product V _R (= 422 L), freezer rated internal volume V _F (= 180 L), water specific heat C _W (= 4.186 kJ / kg ° C.), ice specific heat C _i (= 2.05 kJ / kg ° C.) ), The solidification latent heat of water L _W (= 333.6 kJ / kg), {A _Revp × ( _{TR_keep} −T _{Revp_ave} )} / {A _{Fevp × (T F_keep -T Fevp_ave)}} × {4 × V F × (C W × T out -C i × T F_keep + L W)} / [12 × V R × {C W × (T out -T R_keep) }] Is 1.78, which is higher in R _F / R _R (= 1.94) By controlling in this way, a large-capacity freezer room and practical cooling performance can be obtained. Both can be achieved (details will be described later).

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

  The refrigerator of the present embodiment includes a refrigerator compartment 2 (first refrigerator temperature zone chamber), a vegetable compartment 6 (second refrigerator temperature zone chamber), and a freezer compartment 7, and a refrigerator evaporator 14a at the back of the refrigerator compartment 2 is provided. (First evaporator) and refrigeration blower 9a (first blower), and a freezing evaporator 14b (second evaporator) and a freezing fan 9b (second blower) on the back of the freezer compartment 7, Refrigeration air passage 111 (first air passage) for circulating the cooling air heat-exchanged with refrigeration evaporator 14a by driving the blower into refrigeration chamber 2, and heat exchange with refrigeration evaporator 14b by driving refrigeration fan 9b An air flow blocking means (not shown) that includes a frozen vegetable air passage 112 (second air passage) for circulating cooling air to the freezer compartment 7 and the vegetable compartment 6 and that interrupts the air flow between the first air passage and the second air passage ( A heat insulating partition wall 28) is provided. As a result, the vegetable compartment and the refrigerator compartment can be cooled independently. For example, food with high temperature is stored in the vegetable compartment, or food is sandwiched between the vegetable compartment door and the heat insulation box. Even if the load on the vegetable room increases due to reasons such as the fact that it is not necessary to cool the refrigerator room together with the vegetable room, it is possible to suppress excessive cooling of the refrigerator room, so the cooling efficiency of the refrigerator room decreases. It is possible to prevent. Moreover, unlike the structure which cools a vegetable room indirectly with the cold air of a freezer compartment through a partition etc. like patent document 1, since the air which heat-exchanged with the freezing evaporator can be sent and cooled to a vegetable room, It is possible to prevent the cooling efficiency of the freezer compartment from being lowered by maintaining the freezer compartment at an excessively low temperature. That is, since the load of a part of the storage rooms is cooled, a refrigerator in which the cooling efficiency of the entire refrigerator is unlikely to occur, that is, a refrigerator having a high cooling efficiency as the entire refrigerator is obtained.

  The refrigerator according to the present embodiment includes the refrigerator compartment 2 (first refrigerator compartment) having the maximum rated internal volume among the refrigerator compartment 2 (first refrigerator compartment), the freezer compartment 7, and the vegetable compartment 6 (second refrigerator compartment). The refrigeration air passage 111 (first air passage) through which the cooling air heat-exchanged with the refrigeration evaporator 14a flows to the refrigeration chamber 2 and the cooling air heat-exchanged with the refrigeration evaporator 14b in the freezing compartment 7 And a frozen vegetable air passage 112 (second air passage) that circulates in the vegetable compartment 6, and air flow blocking means (heat insulating partition wall 28) that blocks air flow between the refrigerated air passage 111 and the frozen vegetable air passage 112. It has. In general, the larger the rated internal volume is, the more the food can be stored by the user. Therefore, a storage room with a large rated internal volume often has a large cooling load. Therefore, among the refrigerator compartment 2 (first refrigerator temperature zone room), the freezer compartment 7, and the vegetable compartment 6 (second refrigerator temperature zone compartment), a refrigerator air passage for flowing cooling air to the refrigerator compartment 2 having the maximum rated internal volume. By providing air flow blocking means (heat insulating partition wall 28) so that air does not flow between 111 and the frozen vegetable air passage 112, other freezer compartments are affected by the load of the storage compartment having the maximum rated internal volume. It is possible to prevent the food in the vegetable room or the like from being warmed, and the refrigerator has a high cooling efficiency.

  The refrigerator according to the present embodiment is located in the refrigeration air passage 111 (first air passage) through which cooling air flows to the refrigerating room 2 (first refrigerating temperature zone room) which is the uppermost storage room, and in the lower stage of the refrigerating room 2. A freezing vegetable air passage 112 (second air passage) for allowing cooling air to flow through the freezer compartment 7 and the vegetable compartment 6 and shutting off air flow between the refrigerated air passage 111 and the frozen vegetable air passage 112 Means (heat insulating partition wall 28) are provided. Generally, in an environment where a refrigerator is installed (for example, a kitchen), when air is not actively stirred by an air conditioner or the like, a temperature distribution (temperature stratification) in the vertical direction is formed, and the air is more upward. There is a tendency for the temperature to rise. Therefore, the uppermost storage room is likely to have a higher temperature when the door is opened and closed, and the load is likely to increase. Therefore, the refrigerator of the present embodiment includes a refrigeration air passage 111 through which cooling air flows to the refrigeration room 2 (first refrigeration temperature zone room) that is the uppermost storage room, the freezing room 7 that is the lower storage room, and By providing an air flow blocking means (heat insulating partition wall 28) so that air does not flow between the frozen vegetable air passages 112 through which the cooling air flows to the vegetable compartment 6, other effects can be obtained due to the load of the uppermost storage chamber. It is possible to make it difficult for food in the storage room (freezer room or vegetable room) to be warmed, resulting in a refrigerator with high cooling efficiency.

  As in the refrigerator of this embodiment, in the refrigerator arranged in the order of the refrigerator compartment (freezer temperature zone), the freezer compartment (freezer temperature zone), and the vegetable compartment (refrigerator temperature zone chamber) from the top, Since the freezing room adjacent to the room (freezing temperature zone room) is a storage room that is maintained at a low temperature, the food in the freezing room is likely to be warmed due to the influence of the load flowing into the refrigerating room. That is, the provision of the air flow blocking means (the heat insulating partition wall 28) for blocking the flow of air between the refrigerated air path 111 and the frozen vegetable air path 112 means that the refrigeration room (freezing temperature zone room), freezing room ( This is particularly effective in refrigerators that are arranged in the order of a freezing temperature zone) and a vegetable room (refrigeration temperature zone).

  The refrigerator of the present embodiment has a refrigeration air passage 111 (first air passage) for circulating cooling air to the refrigeration chamber 2 (first refrigeration temperature zone chamber) that is a storage chamber in which the entire circumference of the seal member (packing) is maximum. ), And a frozen vegetable air passage 112 (second air passage) for allowing cooling air to flow through the freezer compartment 7 and the vegetable compartment 6, and air that interrupts the air flow between the refrigerated air passage 111 and the frozen vegetable air passage 112. A flow blocking means (heat insulating partition wall 28) is provided. In the door seal portion, a minute gap may be generated due to food or food packaging material being sandwiched, and the load may increase due to the inflow and outflow of outside air and storage room air. Since the longer the seal length between the door and the heat insulating box, that is, the longer the entire circumference of the seal member, such a situation is more likely to occur. Therefore, the refrigerator of this embodiment has a seal member (packing) A refrigerated air passage 111 for circulating cooling air to the refrigerated room 2, which is a storage room having the maximum perimeter, and a frozen vegetable style for circulating cooling air to the freezing room 7 and the vegetable room 6 located in the lower stage of the refrigerated room 2 By providing an air flow blocking means (heat insulating partition wall 28) that blocks the flow of air between the passages 112, other storages are caused by the influence of the load of the storage chamber that maximizes the total circumference of the seal member (packing). It is possible to prevent a situation where food in the room (freezer room or vegetable room) is warmed, and the refrigerator has a high cooling efficiency.

In the refrigerator of this embodiment, during the stable cooling operation, the maintenance temperature of the refrigerator compartment 2 is T _{R_keep} (about 4 ° C in the case of setting “medium”), and the maintenance temperature of the freezer compartment 7 is T _{F_keep} (setting “medium”). When the average temperature of the refrigeration evaporator 14a during the refrigeration operation is T _{Revp_ave} , the evaporator temperature adjusting means (the compressor 24 and the compressor 24 and the following equation 1) is satisfied. The rotational speed of the refrigeration fan 9a) is controlled.

In general, in the refrigeration cycle, controlling the rotation speed of the blower that blows air to the compressor and evaporator so that the time average temperature of the evaporator during cooling operation is higher, the refrigeration cycle coefficient of performance improves and the cooling efficiency increases. . Therefore, raising the time average temperature of the evaporator when cooling the refrigerator compartment where the temperature maintained is high is effective for improving the cooling efficiency. However, if there is a route through which the cooling air that cools the refrigerator compartment flows to the freezer compartment, the temperature of the freezer compartment that is maintained at a low temperature will rise. Could not be high. Therefore, the refrigerator of the present embodiment is provided with air flow blocking means (heat insulating partition wall 28) that blocks the flow of air between the refrigerated air path 111 and the frozen vegetable air path 112, and includes the compressor 24 and the refrigeration fan. By controlling the rotational speed of 9a, the time average temperature of the refrigeration evaporator during the refrigeration operation is sufficiently increased, and the refrigerator shown in (Equation 1) is satisfied, so that the refrigerator has high cooling efficiency. When there are a plurality of freezer compartments and the maintenance temperature _ranges over a plurality of temperatures, the temperature of the storage compartment having the lowest temperature may be set to _{TF_keep} in (Equation 1).

In the refrigerator of this embodiment, during the stable cooling operation, 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 the refrigerating operation is ΔT (= T _{R_keep−} T _{Revp_ave} ). When the refrigeration cycle theoretical coefficient of performance with respect to temperature is COP _th , the evaporator temperature adjusting means (the compressor 24 and the refrigeration fan 9a) is controlled so as to satisfy (Equation 2). As a result, the cooling operation can be carried out efficiently within a range in which the effectiveness of air volume improvement is high.

The reason will be described with reference to FIGS. FIG. 11 (a) shows the relationship between the theoretical cycle performance coefficient COP _th (coefficient of performance when the compressor efficiency is 100%) and the refrigeration evaporator temperature, and the difference between the refrigeration chamber maintenance temperature _{TR_keep} and the evaporator temperature T _evp . _Is a graph showing an inverse number ΔT ⁻¹ (= 1 / (T _{R_keep} −T _evp )). FIG. 11B shows a function (= d (COP _th ) / dT _evp −d (ΔT ⁻¹ ) / dT _evp ) _obtained by differentiating the difference between ΔT ⁻¹ and COP _th with the evaporator temperature T _evp. It is a graph.

Here, how to obtain the theoretical coefficient of performance COP _th shown in FIG. 11A will be described with reference to FIG. FIG. 12 is a Mollier diagram showing an operation state of a refrigeration cycle of a general refrigerator. The pressure loss in the piping is ignored, and the pressure on the low pressure side (evaporator side) is constant at a pressure determined by the evaporator temperature (evaporation temperature), thereby determining the state of refrigerant sucked by the compressor (state 1). On the high pressure side (condenser side), the outside air temperature is set as the condensation temperature (temperature in the two-phase region), and the pressure determined by the condensation temperature is constant. Also, the refrigerant state at the condenser outlet (capillary tube inlet) is saturated liquid (state 3), the refrigerant state at the evaporator outlet is saturated vapor (state 5), and the capillary tube and the piping from the evaporator to the compressor are completely heated. As the one to be exchanged (operation of the contact portion 57a in FIG. 4), the temperature of the compressor suction refrigerant is set as the condenser outlet temperature (state 1). Also, assuming that the efficiency of the compressor is 100% (adiabatic compression), the compressor discharge state (state 2) is determined, and the heat is completely exchanged between the capillary tube and the piping from the evaporator to the compressor ( From Δh1 = Δh2) in FIG. 4, the refrigerant state (state 4) at the evaporator inlet is determined. Thus, by determining the outside air temperature and the evaporator temperature, the theoretical performance coefficient COP _th is set as the ratio of the theoretical cooling capacity Q _th to the theoretical compression power W _th (COP _th = Q _th / W _th ). Can be calculated. The theoretical coefficient of performance COP _th is an index representing 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. 11A is 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 exchange heat amount in the evaporator. Ignoring changes in temperature efficiency (the difference between the evaporator inlet air temperature and the evaporator outlet air temperature divided by the difference between the evaporator inlet air temperature and the evaporator temperature), A relationship is derived that is proportional to the inverse of the difference between the air temperature and the evaporator temperature. By using the refrigerating room maintenance temperature T _{R_keep} as the air temperature, ΔT ⁻¹ shown in FIG. 11A is calculated and becomes an index representing the magnitude of the air volume for obtaining a predetermined exchange heat amount. In addition, ( _DELTA ) T- ¹ shown to _Fig.11 (a) is calculated by making cold room maintenance temperature _{TR_keep} into 4 _degreeC .

Both COP _th and ΔT ⁻¹ shown in FIG. 11A increase monotonously with the increase in the evaporator temperature T _evp , but the gradients of both 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 represents the difference in gradient between the two. That is, in the graph of FIG. 11B, in the range where the gradient is positive (the range in which the evaporator temperature T _evp is lower than about −1 ° C.), the increasing rate of COP _th with respect to the increase in the evaporator temperature T _evp is _greater. , higher than the rate of increase [Delta] T ^-1 for increase in the evaporator temperature T _evp, it can be said that the advantageous to increase the evaporator temperature T _evp to enhance COP _th. On the other hand, the range where the slope is negative (evaporator temperature T _evp higher range than about -1 ° C.), the direction of increase of the COP _th relative increase in the evaporator temperature T _evp, for increase in the evaporator temperature T _evp This indicates that the rate of increase is lower than ΔT ⁻¹ , and it can be said that the effectiveness of improving the air flow required to raise the evaporator temperature T _evp is reduced. That is, control is performed so that d ² (COP _th ) / dT _evp ² −d ² (ΔT ⁻¹ ) / dT _evp ² ≧ 0 so that the _{graph of} FIG. This means that the refrigerator is operated in a range where the effectiveness of air flow improvement is high. Therefore, in the refrigerator of the present embodiment, the evaporator temperature T _evp in FIG. 11 is controlled as the time average temperature T _{Revp_ave} of the refrigeration evaporator 14a during the refrigeration operation _so as to satisfy (Equation 2), Cooling operation is carried out efficiently in the range where the effectiveness of air flow improvement is high.

  The refrigerator of the present embodiment has an operation mode in which the driving time of the refrigeration fan 9a in the refrigeration chamber 2 having the maximum rated internal capacity is longer than the driving time of the refrigeration fan 9b during the stable cooling operation. As a result, the refrigerator compartment 2 having the maximum rated internal volume can be made a storage room with little temperature unevenness and high storage stability. In general, a state where a positive air flow is generated by driving the air blowing means is called forced convection, and a weak air current caused by a temperature difference (density difference) without air blowing by the air blowing means is called natural convection. When forced convection is generated in the space by air blowing means, air is actively moved to achieve temperature equalization in the space. When the air blowing means is stopped, natural convection occurs and Since the movement of air is difficult to occur, temperature unevenness is likely to be formed, particularly in a space with a large volume. If the temperature unevenness is large, a problem that the storage stability of the food decreases depending on the place where the food is stored is likely to occur. Therefore, the refrigerator of this embodiment includes an operation mode in which the driving time of the refrigeration fan 9a in the refrigeration chamber 2 having the maximum rated internal volume is controlled to be longer than the driving time of the refrigeration fan 9b. The refrigerated room 2 is a storage room with little temperature unevenness and high storability.

  In addition, the refrigerator of the present embodiment has an operation mode in which the driving time of the refrigeration fan 9a in the refrigeration room 2 which is the storage room having the maximum height is longer than the driving time of the refrigeration fan 9b. In general, since the temperature distribution tends to increase as the space having a larger height dimension, in the refrigerator of the present embodiment, the driving time of the refrigeration fan 9a in the refrigeration room 2, which is the storage room having the maximum height dimension, is a refrigeration fan. By providing an operation mode that is longer than the drive time of 9b, the refrigerator compartment 2 is a storage room with little temperature unevenness and high storage stability.

  In the refrigerator of this embodiment, the refrigerator outlet 11a of the refrigerator compartment air passage 11 provided on the back of the refrigerator compartment is opened upward (cold air directing means) to blow out the air directed upward. In general, if food stored in the storage room obstructs the flow of cooling air, the temperature in the storage room may become uneven, or the air flow resistance may increase and the air volume may decrease, resulting in a decrease in cooling efficiency. is there. Therefore, the main refrigerator outlet 11a of the refrigerator compartment air passage 11 is opened upward (cold air directing means), and the upwardly directed air is blown out so that the cooling air is indicated by an arrow in FIG. In addition, since the food flows forward along the ceiling surface of the refrigerator compartment 2, even if a large amount of food is stored in the refrigerator compartment 2, the flow of cooling air is less likely to be obstructed by the food, and the temperature in the storage compartment is uneven. , It becomes a refrigerator with high cooling efficiency that is unlikely to cause a situation in which the air flow resistance increases and the air volume decreases. In the refrigerator of the present embodiment, the opening provided in the refrigerator compartment air passage 11 is only the refrigerator compartment outlet 11a opened upward, but blows out forward or sideward. Other openings may be provided. In this case, the above-described effect can be obtained by making the opening area (total area) of the discharge ports opened upward larger than the sum of the opening areas of the other discharge ports.

  The refrigerator of the present embodiment is provided with a door pocket 33a having an opening position higher than the shelf 34a located at the uppermost stage of the refrigerator compartment 2, and the refrigerator outlet 11a of the refrigerator compartment air passage 11 provided on the back of the refrigerator compartment is directed upward. Opening (cold air directing means), the air directed upward is blown out. As a result, the cooling air flows along the ceiling surface of the refrigerator compartment 2 toward the door pocket 33a having a higher opening position than the shelf 34a located at the uppermost stage of the refrigerator compartment 2, as indicated by an arrow in FIG. The door pocket 33a can be cooled satisfactorily.

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

  The refrigerator of the present embodiment includes a refrigerator compartment 2 (first refrigerator temperature zone chamber), a vegetable compartment 6 (second refrigerator temperature zone chamber), and a freezer compartment 7, and a refrigerator evaporator 14a at the back of the refrigerator compartment 2 is provided. (First evaporator) and refrigeration blower 9a (first blower), and a freezing evaporator 14b (second evaporator) and a freezing fan 9b (second blower) on the back of the freezer compartment 7, Refrigeration air passage 111 (first air passage) for circulating the cooling air heat-exchanged with refrigeration evaporator 14a by driving the blower into refrigeration chamber 2, and heat exchange with refrigeration evaporator 14b by driving refrigeration fan 9b An air flow blocking means (not shown) that includes a frozen vegetable air passage 112 (second air passage) for circulating cooling air to the freezer compartment 7 and the vegetable compartment 6 and that interrupts the air flow between the first air passage and the second air passage ( A heat-insulating partition wall 28) and a deodorizing member 91 in contact with the air flowing through the refrigerated air passage 111 are provided. Thereby, when the foodstuff etc. which generate | occur | produce an odor in the refrigerator compartment 2 are accommodated, since it can prevent that an odor component circulates to other storage rooms (freezer compartment 7 and vegetable compartment 6) with cooling air, refrigerator compartment 2 It is possible to prevent odors from being transferred to foodstuffs in the other storage rooms (freezer room 7 and vegetable room 6). Moreover, since the cooling air containing an odor component circulates only through the refrigerating 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 that comes into contact with the air flowing through the refrigerated air passage 111, and a stable cooling operation. The operation mode is such that the drive time of the refrigeration fan 9a in the refrigerator compartment 2 is longer than the drive time of the refrigeration fan 9b. When the refrigeration fan 9a is driven, since more air passes through the deodorizing member 91, the deodorizing action is increased. Therefore, an operation mode in which the driving time of the refrigeration fan 9a is longer than the driving time of the refrigeration fan 9b is provided. Thus, a refrigerator having a higher deodorizing effect can be obtained.

  The refrigerator of the present embodiment includes a storage room in the order of the refrigerator compartment 2 (first refrigerator temperature zone), the freezer compartment 7 (freezer temperature zone compartment), and the vegetable compartment (second refrigerator temperature zone compartment) from above. 7 is provided with a freezing evaporator 14b (second evaporator), the volume of the freezing evaporator 14b is set to 3% or less of the rated internal volume of the freezing room 7, and the rated internal volume of the freezing room 7 is fully rated. The refrigeration evaporator 14a (first evaporator) is provided at the back of the refrigeration chamber 2 which is a refrigeration temperature zone. Thereby, while providing a large-capacity freezer compartment in the refrigerator center part, the refrigerator which exhibits favorable practical cooling performance can be provided. The reason will be explained below.

  In general, frost grows on the surface of the evaporator that cools the freezing temperature zone. When frost grows on the surface of the evaporator, the flow resistance passing through the evaporator becomes narrower and the resistance to ventilation increases and the thermal resistance increases due to the frost layer between the evaporator surface and the air. Replacement performance decreases and cooling efficiency decreases. Therefore, the defrosting operation is performed so as not to cause a problem due to a decrease in the heat exchange performance of the evaporator. During the defrosting operation in which frost is released by raising the temperature of the evaporator by a heating means such as a heater, the freezing temperature zone cannot be cooled. Accordingly, if the heat exchange performance of the evaporator is likely to decrease due to frost growth, defrosting operation in which the temperature of the freezing temperature zone rises frequently is performed. In other words, it is a problem to obtain a stable cooling performance of the freezing temperature zone chamber to make it difficult for the heat exchange performance to decrease due to frost growth. For example, in a refrigerator provided with a cooler (evaporator) that is a heat exchanger for cooling each storage chamber in a cooling chamber (evaporator chamber) behind the freezer compartment, such as a refrigerator described in Patent Document 1. In general, the evaporator is designed so as to suppress a decrease in heat exchange performance due to frost growth by sufficiently increasing the size of the evaporator (evaporator volume). On the other hand, the volume of the freezing evaporator cannot be reduced to 3% or less of the rated internal volume of the freezing temperature zone, and the rated internal volume of the freezing temperature zone cannot be increased to 28% or more of the total rated internal volume. It was.

  In general, the higher the air temperature, the greater the amount of water contained in the air (the higher the absolute humidity). Therefore, if an evaporator that cools the refrigeration temperature zone and the refrigeration temperature zone is provided, the refrigeration temperature zone More water reaches the evaporator from the refrigerated temperature zone where the maintenance temperature is higher than that and becomes frost. Therefore, in the refrigerator of the present embodiment, by adopting a configuration in which the refrigeration evaporator 14b is provided at the back of the freezer compartment 7 and the refrigeration evaporator 14a is provided at the back of the refrigerator compartment 2, the freezer compartment at the center of the refrigerator is employed. 7 Even if the evaporator installed on the back of 7 is downsized to 3% or less of the rated internal volume of the freezer compartment 7 and the rated internal volume of the freezing temperature zone is expanded to 28% or more of the total rated internal volume, Since frost does not grow due to moisture from the refrigerator compartment 2 containing a large amount of moisture (absolute humidity), the evaporator is less susceptible to a decrease in heat exchange performance and can exhibit stable cooling performance.

  Moreover, the 1st evaporator is provided in the refrigerator temperature zone room with a large rated internal volume among the refrigerator compartment 2 and the vegetable compartment 6 used as a refrigerator temperature zone room. As a result, the refrigerator compartment 2 where the load tends to be large due to the large internal volume can be efficiently cooled, so that a refrigerator having both a large-capacity freezer compartment and good practical cooling performance can be obtained.

The air-side heat transfer area A _Fevp refrigerator freezer evaporator 14b in the present embodiment, is made larger than the air-side heat transfer area A _REVP of refrigerating evaporator 14a. In general, when the air-side heat transfer area of the evaporator is increased, heat exchange between the air and the refrigerant is promoted to increase the cooling capacity. Therefore, the air-side heat transfer area A _Fevp refrigeration evaporator 14b, and larger than the air-side heat transfer area A _REVP of refrigerating evaporator 14a, a freezing chamber 7 is possible to further increase the cooling capacity during cooling , Achieving both a large-capacity freezer and good practical cooling performance.

In the refrigerator of the present embodiment, the air side heat transfer areas per unit volume of the refrigeration evaporator 14a and the refrigeration evaporator 14b are A _Revp / V _Revp = 0.673 m ² / L and A _Fevp / V _{Fevp, respectively.} = 0.384M a ² / L, 0.25m ² / L or more, and the following value 0.96 m ² / L. In general, frost grows on the air-side heat transfer surface of the evaporator. Therefore, if the air-side heat transfer area is increased with respect to the evaporator volume, the flow path is likely to be blocked when frost grows. For this reason, when the growth of frost is large, the heat exchange performance is likely to deteriorate, but when the growth of frost is small, the evaporator has a high heat exchange performance. On the other hand, if the air-side heat transfer area is reduced with respect to the evaporator volume, the flow path is not easily blocked by frost even if frost grows and it is easy to maintain heat exchange performance, but the air-side heat transfer area is reduced. When the frost growth is small, the heat exchange performance per unit volume is low. Accordingly, the refrigerator of this embodiment, refrigerating evaporator 14a, and the air-side heat transfer area per unit volume of the freezer evaporator 14b, 0.25 m ² / L or more, and 0.96 m ² / L or less By doing so, the performance when the growth of frost is large and the performance when the growth of frost is small are made compatible.

Further, the air-side heat transfer area per unit volume (A _Revp / V _Revp ) of the refrigeration evaporator 14a is larger than the air-side heat transfer area (A _Fevp / V _Fevp ) per unit volume of the refrigeration evaporator 14b. It is increased (A _Revp / V _Revp > A _Fevp / V _Fevp ). The frost that has grown on the refrigerating evaporator 14b is dissolved by the refrigerating evaporator defrosting operation that is heated by the defrosting heater 21, and the freezer compartment 7 cannot be cooled during the refrigerating evaporator defrosting operation. On the other hand, the frost grown on the refrigeration evaporator 14a can be dissolved while the refrigeration chamber 2 is cooled by the refrigeration evaporator defrosting operation. Therefore, by making the air side heat transfer area per unit volume of the refrigeration evaporator 14a larger than the air side heat transfer area per unit volume of the refrigeration evaporator 14b, the flow path of the refrigeration evaporator 14b is increased. It is made difficult to be blocked by frost, and the problem that the cooling of the freezer compartment 7 is deteriorated by increasing the frequency of the defrosting operation is prevented.

In the refrigerator of this embodiment, when a practical load is applied to both the freezing temperature zone and the refrigeration temperature zone, the refrigerator is cooled between the time when the load is applied and the practical load is sufficiently cooled. time average temperature T _{Revp_ave} the refrigerating evaporator 14a during operation, the time-averaged temperature T becomes higher as the evaporator temperature control means than _{Fevp_ave} refrigeration evaporator 14b during freezing compartment cooling operation (the compressor 24, refrigeration The fan 9a, the freezing fan 9b, and the vegetable compartment damper 19) are controlled. Generally, the higher the evaporator temperature (evaporation temperature), the higher the coefficient of performance of the refrigeration cycle (the ratio of the endothermic amount to the input of the compressor 24), and the higher the energy saving performance. In order to maintain the freezing chamber 7 at the freezing temperature, the temperature of the freezing evaporator 14b needs to be _lowered. However, since the refrigerating chamber 2 only needs to be maintained at the refrigerating temperature, the temperature T _Revp of the refrigerating evaporator is _reduced. The evaporator temperature adjusting means (the compressor 24, the refrigeration fan 9a, the freezing fan 9b, and the vegetable compartment damper 19) is controlled so as to be higher than the temperature T _Fevp of the evaporator, thereby improving the energy saving performance. .

In the refrigerator of this example, when a practical load was applied to both the freezing temperature zone room and the refrigeration temperature zone room, the maximum value (maximum temperature reached) of the freezing room temperature was less than 0 ° C. ( _TF1 <T _{F1 in} FIG. 10). 0), the evaporator temperature adjusting means (the compressor 24, the refrigeration fan 9a, the freezing fan 9b, and the vegetable compartment damper 19) is controlled. As a result, it is possible to obtain good practical cooling performance while avoiding the occurrence of problems such as the dissolution of food stored in the freezing temperature zone chamber due to the input of the practical load.

  When the practical load is applied to both the refrigeration temperature zone chamber and the refrigeration temperature zone chamber, the refrigerator of the present embodiment has a practical load cooling interval from when the load is applied until the practical load is sufficiently cooled. The evaporator temperature adjusting means (the compressor 24, the refrigeration fan 9a, the freezing fan 9b, and the vegetable compartment damper 19) is controlled so that a plurality of maximum values of the freezing room temperature gradually decrease. As a result, the temperature of the freezer rises and the problem of freezing the frozen food hardly occurs, and the refrigerator has high practical cooling performance.

When the practical load is applied to both the refrigeration temperature zone chamber and the refrigeration temperature zone chamber, the refrigerator of the present embodiment has a practical load cooling interval from when the load is applied until the practical load is sufficiently cooled. The refrigerator operating ratio is R _R , the refrigerator operating ratio is R _F , the outside air temperature is T _out (° C.), the air side heat transfer area of the evaporator 14a is A _Revp (m ² ), and the evaporator is The time average temperature during refrigerating operation of 14a is T _{Revp_ave} (° C), the refrigerating room maintenance temperature is T _{R_keep} (° C), the air side heat transfer area of the refrigerating evaporator 14b is A _Fevp (m ² ), and the refrigerating evaporator. In the freezer cooling operation of 14b, the time average temperature is T _{Fevp_ave} (° C), the freezer maintenance temperature is T _{F_keep} (° C), the refrigerator compartment rated internal volume is V _R (L), and the freezer compartment rated internal volume is V _F ( L), the specific heat of water _{C W (kJ / kg ℃)} , the specific heat of ice _{C i (kJ / kg ℃)} , the latent heat of solidification of water _{L W} (kJ / As g), and it controls the (so as to satisfy the equation 3), an evaporator temperature control means (compressor 24, the refrigerating fan 9a, freezing fan 9b, vegetable compartment damper 19).

As a result, the refrigerator has both a large-capacity freezer and good practical cooling performance. The reason will be explained below. Generally, in a refrigerator, not only heat intrusion through the wall surface of the heat insulation box but also an unsteady load increase such as a door opening / closing operation of a user and insertion of food with high temperature occurs. In particular, in a refrigerator equipped with a refrigerated temperature storage room and a freezing temperature storage room, even if a situation occurs in which a large amount of food is put into both storage rooms at the same time, the predetermined maintenance temperature is quickly reached. Need to cool down. However, since the temperature zone to be maintained is different between the refrigerated temperature zone and the freezing temperature zone, one of the storage chambers is apt to be cooled, or only one of the storage chambers is excessively cooled. That is, it is a problem to cool the refrigeration temperature zone chamber and the freezing temperature zone chamber in a balanced manner. Especially in refrigerators equipped with a refrigerator compartment, freezer compartment, and vegetable compartment from the top, the evaporator installed at the back of the freezer compartment is downsized to 3% or less of the rated internal volume of the freezer compartment, and the freezer compartment rated internal volume is increased. If the capacity is increased to 28% or more of the total rated internal volume, the balance between the load in the refrigerator compartment and the freezer compartment and the balance of the cooling capacity will be lost, one of the storage rooms will be cold, or only one of the storage rooms will be excessive. The problem of cooling became apparent, and there was a situation where good cooling performance could not be demonstrated. Therefore, in the refrigerator of the present embodiment, when a practical load is applied to the refrigerator compartment 2 and the freezer compartment 7, the refrigerator operation / frozen vegetable operation and the refrigerator operation are performed so as to satisfy (Equation 3). Therefore, both a large-capacity freezer room and practical cooling performance are achieved.
In Formula 3, A _Fevp × ( _{TF_keep−} T _{Fevp_ave} ) is an index of the amount of exchange heat in the refrigeration evaporator 14b, and A _Revp × ( _{TR_keep−} T _{Revp_ave} ) is the amount of exchange heat in the refrigeration evaporator 14a. 12 × V _R × {C _W × (T _out −T _{R_keep} )} is an index of an endothermic amount (cooling load) required for cooling a practical load put into the refrigerator compartment, and 4 × V _F × { C _W × T _out −C _i × T _{F_keep} + L _W } is an index of an endothermic amount (cooling load) necessary for cooling a practical load put into the refrigerator compartment. In other words, from the right side, the minimum required freezer cooling (freezer room cooling operation or freezer cooling operation) considering the ratio of the exchange heat quantity in the refrigeration evaporator and the freezing evaporator and the ratio of the cooling load of the practical load. ) To the refrigerator compartment cooling operation is calculated. In the refrigerator of this embodiment, since the freezer compartment cooling operation is controlled so as to be higher than the ratio, a large-capacity freezer can be used even when a large load is simultaneously applied to the refrigerator compartment and the freezer compartment. This makes it possible to achieve both a room and practical cooling performance. Incidentally, 12 × _{V R} of the right side of (Equation 3), and, 4 × _{V F} is refrigeration temperature zone compartment (freezer compartment and a vegetable compartment) 1L per 12g, water (initial temperature of the freezing temperature zone compartment 1L per 4g is This means that the outside air temperature) is put into the refrigerator compartment and the freezer compartment, respectively, and the amount of load defined in JIS C9801-3: 2015 is taken into account in consideration of general usage.
Further, since the refrigerator of this embodiment has an automatic ice making function, it is assumed that the load fluctuates when the user uses the automatic ice making function. In this case, since the ice making water tank is installed in the refrigerator compartment 2, the load of the refrigerator compartment 2 increases. However, since freezing does not occur in the refrigerating chamber 2 maintained in the refrigerated temperature zone, only a sensible heat load is applied. When water is supplied from the refrigerated chamber 2 to the ice making chamber 3 in the freezing temperature zone, the sensible heat is frozen. In addition to this, latent heat is also a burden. Therefore, since the load on the freezer compartment 7 is larger than that in the refrigerator compartment 2, the freezing temperature zone is preferentially cooled by controlling as shown in (Equation 1), so even when the automatic ice making function is used. , Practical cooling performance can be easily maintained.

Note that the refrigerator compartment maintenance temperature T _Rkeep and the freezer compartment maintenance temperature T _Fkeep in (Equation 1) and (Equation 3) include the refrigerator compartment during the stable cooling operation measured based on the method defined in JIS C9801-1: 2015. 2 and the temperature average value of the freezer compartment 7 may be used. The time average temperature _{(T Revp_ave, T Fevp_ave)} of the refrigerating evaporator 14a and the freezer evaporator 14b refrigerating evaporator temperature _{T REVP} and freezing evaporator temperature _{T Fevp} for calculating the refrigerating evaporator What is necessary is just to measure and use the temperature of the inflow part vicinity of the refrigerant | coolant pipes 97a and 97b of 14a and the evaporator 14b for freezing.

  The above is an example showing a mode for carrying out the present invention. In addition, this invention is not limited to the Example mentioned above, Various modifications are included. For example, in the refrigerator of the present embodiment, the heat insulating partition wall 28 is employed as the air flow blocking means in order to more reliably block the air flow. However, if the function of blocking the air flow is obtained, the partition member A state in which the air flow is shut off by providing a damper in a part of and closing the damper may be configured. In the refrigerator of this embodiment, the compressor 24, the refrigeration fan 9a, and the refrigeration fan 9b are used as the evaporator temperature adjusting means. However, if the evaporator temperature can be adjusted, the heat radiating means can be used as other means. A fan for controlling the heat radiation amount and an expansion valve for varying the throttle resistance may be used as the evaporator temperature adjusting means. That is, the above-described embodiments are described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.

1 Refrigerator 2 Refrigerated room (first refrigerated temperature room)
2a, 2b Refrigeration room door 3 Ice making room 4 Upper freezing room 5 Lower freezing room Freezing room 3a, 4a, 5a Freezing room door 6 Vegetable room (second refrigeration temperature zone room)
6a Vegetable room door 7 Freezer room (generic name for 3, 4 and 5)
8a Refrigerator evaporator room (first evaporator storage room)
8b Evaporator chamber for refrigeration (second evaporator storage chamber)
9a Refrigeration fan (first blower)
9b Refrigeration fan (second blower)
DESCRIPTION OF SYMBOLS 10 Heat insulation box 10a Outer box 10b Inner box 11 Refrigeration room air outlet 11a Refrigeration room air outlet 12 Freezer room air outlet 12a Freezer room air outlet 13 Vegetable room air outlet 13a Vegetable room outlet 14a Refrigerator evaporator (first evaporator) )
14b Refrigerating evaporator (second evaporator)
15a, 15b 15c Refrigeration room return air passage 16 Hinge cover 17 Freezer compartment return port 18 Vegetable room return air passage 18a Vegetable room return port 19 Vegetable room damper 21 Radiant heaters 22a, 22b Drainage ports 23a, 23b 樋 24 Compressor 26 Outside the chamber Fan 27a Refrigeration drain pipe 27b Refrigeration drain pipe 28, 29, 30 Insulating partition wall 31 Control board 32 Evaporating dish 35 Chilled room 39 Machine room 40a Refrigeration evaporator temperature sensor 40b Refrigeration evaporator temperature sensor 41 Refrigeration room temperature sensor (First load detection means)
42 Freezer temperature sensor (second load detection means)
43 Vegetable room temperature sensors 50a, 50b External radiator (heat dissipation means)
50c Condensation suppression piping (heat dissipation means)
51 Dryer 52 Three-way valve (refrigerant control means)
53a Capillary tube for refrigeration (pressure reduction means)
53b Capillary tube for freezing (pressure reduction means)
54a Refrigeration gas / liquid separator 54b Refrigeration gas / liquid separator 55a, 55b Heat exchange unit 56 Check valve 91 Deodorizing members 95a, 95b Refrigeration chamber packing (first seal member)
96a, 96b, 96c Freezer compartment packing (second seal member)
97 Vegetable room packing (third seal member)
101 Head heater 102 Drain pipe upper heater 103 Drain pipe lower heater

Claims (6)

  A first refrigeration temperature zone chamber, a second refrigeration temperature zone chamber, and a refrigeration temperature zone chamber; a first evaporator and a first blower on the back of the first refrigeration temperature zone chamber; In a refrigerator provided with a second evaporator and a second blower at the back of the refrigerated temperature zone, the first chilled temperature zone chamber is configured to circulate air exchanged with the first evaporator by driving the first blower. A first air passage, and a second air passage through which air exchanged with the second evaporator by driving the second blower is circulated to the refrigeration temperature zone chamber and the second refrigeration temperature zone chamber, A refrigerator comprising air flow blocking means for blocking air flow between a path and the second air path.   A first storage chamber, a second storage chamber, and a third storage chamber are provided in the heat insulation box, and the rated internal volume of the first storage chamber is greater than any of the rated internal volumes of the second storage chamber and the third storage chamber. In a large refrigerator, a first evaporator and a first blower are provided in a region where the first storage chamber is partitioned, and a second evaporator is disposed in the region where the second storage chamber or the third storage chamber is partitioned. And a second air blower, a first air passage through which air exchanged heat with the first evaporator by driving the first air blower flows to the first storage chamber, and the second evaporation by driving the second air blower A second air passage through which the air heat-exchanged with the vessel is circulated to the second storage chamber and the third storage chamber, and an air flow that blocks air flow between the first air passage and the second air passage A refrigerator comprising a shut-off means.   A heat insulation box is provided with a first storage chamber, a second storage chamber, and a third storage chamber from above, and the first evaporator and the first evaporator are disposed in a region where the first storage chamber is defined inside the heat insulation box. Air provided with a blower, having a second evaporator and a second blower in a region where the second storage chamber or the third storage chamber is partitioned, and exchanging heat with the first evaporator by driving the first blower And a second air passage through which air exchanged with the second evaporator by driving the second blower is circulated to the second storage chamber and the third storage chamber. And a air flow blocking means for blocking air flow between the first air path and the second air path.   A first storage chamber, a second storage chamber, and a third storage chamber are provided in a heat insulating box that opens forward, and a first storage chamber door that opens and closes the first storage chamber, and a first storage chamber that opens and closes the second storage chamber. Two storage chamber doors, a third storage chamber door that opens and closes the third storage chamber, a first seal member that secures a sealing property between the first storage chamber door and the heat insulation box, A second seal member that secures a seal between the second storage chamber door and the heat insulation box, and a third seal member that secures a seal between the third storage chamber door and the heat insulation box. The first storage chamber is defined in a refrigerator in which the entire circumference of the first seal member is greater than both the overall circumference of the second seal member and the overall circumference of the third seal member A first evaporator and a first blower are provided in the region, and the second storage chamber or the third storage chamber is partitioned in the second region. A first air passage for supplying air to the first storage chamber through the heat exchange with the first evaporator by driving the first blower; and the first blower by driving the second blower. A second air passage through which air exchanged with the two evaporators flows through the second storage chamber and the third storage chamber, and blocks air flow between the first air passage and the second air passage. A refrigerator comprising air circulation blocking means.   By controlling at least the compressor and the first blower, the time average temperature of the first evaporator during the refrigeration operation in the stable cooling operation, the maintenance temperature of the refrigeration temperature zone chamber and the first refrigeration temperature zone chamber The refrigerator according to any one of claims 1 to 4, wherein the refrigerator is not less than an arithmetic average value of the maintenance temperature. By controlling at least the compressor and the first blower, the difference between the maintenance temperature T _{R_keep of} the first refrigeration temperature zone chamber and the time average temperature T _{Revp_ave} of the first evaporator during the refrigeration operation in the stable cooling operation 5 is set to ΔT (= T _{R_keep} −T _{Revp_ave} ), and the refrigeration cycle theoretical coefficient of performance with respect to the evaporator temperature is set to COP _th , the following equation is satisfied: Refrigerator.

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