CN110094917B

CN110094917B - Refrigerator with a refrigerator body

Info

Publication number: CN110094917B
Application number: CN201811029402.9A
Authority: CN
Inventors: 河井良二; 额贺晴树; 冈留慎一郎; 小沼智史; 小川真申; 板仓大; 冈田福太郎; 服部圭介; 盐野谦治; 门传阳平
Original assignee: Hitachi Global Life Solutions Inc
Current assignee: Hitachi Global Life Solutions Inc
Priority date: 2018-01-31
Filing date: 2018-09-05
Publication date: 2024-07-23
Anticipated expiration: 2038-09-05
Also published as: CN112378146A; CN112378146B; CN110094917A

Abstract

The invention provides a refrigerator with a refrigerating chamber, a freezing chamber and a vegetable chamber, which can exert high cooling efficiency as a whole even if the load of a part of the storage chamber is increased. The refrigerator is provided with a first refrigeration temperature zone chamber, a second refrigeration temperature zone chamber and a freezing temperature zone chamber, wherein a first evaporator and a first blower are arranged at the back of the first refrigeration temperature zone chamber, and a second evaporator and a second blower are arranged at the back of the freezing temperature zone chamber or the second refrigeration temperature zone chamber, and the refrigerator is provided with: a first air passage configured to circulate the air heat-exchanged with the evaporator to the first refrigeration temperature zone chamber by driving the first blower; and a second air passage through which air having exchanged heat with the second evaporator flows into the freezing temperature zone chamber and the second refrigerating temperature zone chamber by driving the second blower, wherein the refrigerator further comprises an air flow shut-off means for shutting off the flow of air between the first air passage and the second air passage.

Description

Refrigerator with a refrigerator body

Technical Field

The present invention relates to a refrigerator.

Background

As a background art in the art, for example, japanese patent application laid-open No. 2006-64256 (patent document 1) is known.

Patent document 1 discloses a refrigerator in which a main body has a contour formed of a heat-insulating box body, and an inner space (i.e., a box interior) of the heat-insulating box body is provided with a refrigerating chamber, an ice chamber, a selection chamber for selecting freezing or refrigerating, a freezing chamber, and a vegetable chamber from above, the refrigerating chamber is cooled by a first evaporator as an evaporator for the refrigerating chamber, the ice chamber, the selection chamber, and the freezing chamber are cooled by a second evaporator as an evaporator for the freezing chamber, and the vegetable chamber is indirectly cooled by cooling air of the freezing chamber via a partition wall or the like between the vegetable chamber and the freezing chamber (for example, fig. 3 of patent document 1).

Prior art literature

Patent literature

Patent document 1: japanese patent laid-open No. 2006-64256

Disclosure of Invention

Problems to be solved by the invention

The refrigerator described in patent document 1 includes a refrigerating chamber, a freezing temperature zone chamber (an ice chamber, a selection chamber, a freezing chamber), and a vegetable chamber, the refrigerating chamber is cooled by an evaporator for the refrigerating chamber, the ice chamber, the selection chamber, and the freezing chamber are cooled by the evaporator for the freezing chamber, and the vegetable chamber provided below the freezing chamber is indirectly cooled by cooling air of the freezing chamber via a partition wall or the like between the vegetable chamber and the freezing chamber.

In the case of indirect cooling, in order to improve the cooling capacity of the vegetable room, it is necessary to promote heat transfer through the partition wall. In general, in order to promote heat transfer through the partition wall, it is effective to enlarge a temperature difference in the space (the freezing chamber and the vegetable chamber) partitioned by the partition wall. Therefore, when the load on the vegetable room is large and the cooling capacity needs to be sufficiently improved due to the high ambient temperature, the high temperature food is stored in the vegetable room, or the gap is generated between the vegetable room door leaf and the heat insulation box due to the sandwiching of the food, etc., the freezing room needs to be excessively maintained at a low temperature, and the cooling efficiency is reduced. Further, the refrigerating chamber connected to the freezing chamber is also indirectly affected by the heat of the freezing chamber by excessively maintaining the freezing chamber at a low temperature, and thus there is a problem in that the cooling efficiency is lowered. That is, in order to cool a load of a part of the storage chamber, there is a problem in that cooling efficiency of the refrigerator as a whole is lowered.

The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a refrigerator including a refrigerating chamber, a freezing chamber, and a vegetable chamber, which can exhibit high cooling efficiency as a whole even when a load of a part of the storage chamber is increased.

Means for solving the problems

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

The present application provides a refrigerator including a first refrigeration temperature zone chamber, a second refrigeration temperature zone chamber, and a freezing temperature zone chamber, wherein a first evaporator and a first blower are provided on a back of the first refrigeration temperature zone chamber, and a second evaporator and a second blower are provided on a back of the freezing temperature zone chamber or the second refrigeration temperature zone chamber, the refrigerator comprising: a first air passage configured to circulate the air heat-exchanged with the evaporator to the first refrigeration temperature zone chamber by driving the first blower; and a second air passage through which air having exchanged heat with the second evaporator flows into the freezing temperature zone chamber and the second refrigerating temperature zone chamber by driving the second blower, wherein the refrigerator further comprises an air flow shut-off means for shutting off the flow of air between the first air passage and the second air passage.

Effects of the invention

According to the present invention, a refrigerator including a refrigerator compartment, a freezer compartment, and a vegetable compartment can be provided, wherein even when a load of a part of the storage compartment is increased, a high cooling efficiency can be exhibited as a whole of the refrigerator.

Drawings

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

Fig. 2 is a cross-sectional view A-A of fig. 1.

Fig. 3 is a B-B cross-sectional view of fig. 2.

Fig. 4 is a schematic view showing a wind path structure of a refrigerator of an embodiment.

Fig. 5 is a schematic view showing a refrigeration cycle structure of a refrigerator according to an embodiment.

Fig. 6 is a diagram showing an evaporator of a refrigerator of an embodiment.

Fig. 7 is a flowchart showing operation control at normal time of the refrigerator of the embodiment.

Fig. 8 is a flowchart showing operation control at the time of high load of the refrigerator of the embodiment.

Fig. 9 is an example of a time chart showing control at normal time of the refrigerator according to the embodiment.

Fig. 10 is an example of a time chart showing control at the time of high load of the refrigerator of the embodiment.

Fig. 11 is a graph showing the relationship among the evaporator temperature, the theoretical coefficient of performance, and the refrigerating chamber temperature of the refrigerator.

Fig. 12 is a mollier chart showing a state of a refrigerating cycle of the refrigerator.

In the figure:

1-refrigerator, 2-refrigerating chamber (first refrigerating temperature zone chamber), 2a, 2 b-refrigerating chamber door fan, 3-ice making chamber, 4-upper layer freezing chamber, 5-lower layer freezing chamber, 3a, 4a, 5 a-freezing chamber door leaf, 6-vegetable chamber (second refrigerating temperature zone chamber), 6 a-vegetable chamber door leaf, 7-freezing chamber (sum of 3, 4, 5), 8 a-refrigerating evaporator chamber (first evaporator housing chamber), 8 b-freezing evaporator chamber (second evaporator housing chamber), 9 a-refrigerating fan (first blower), 9 b-refrigerating fan (second blower), 10-heat insulation box, 10 a-outer box, 10 b-inner box, 11-refrigerating chamber air-sending path, 11 a-refrigerating chamber air-sending port, 12-freezing chamber air-sending path, 12 a-freezing chamber air-sending port, 13-vegetable chamber air-sending path, 13 a-vegetable chamber air-sending port, 14 a-a refrigerating evaporator (first evaporator), 14 b-a freezing evaporator (second evaporator), 15a, 15b, 15 c-a refrigerating chamber return air passage, 16-a hinge cover, 17-a freezing chamber return opening, 18-a vegetable chamber return air passage, 18 a-a vegetable chamber return opening, 19-a vegetable chamber baffle, 21-a radiation heater, 22a, 22 b-a water discharge opening, 23a, 23 b-a water guide pipe, 24-a compressor, 26-an out-of-box fan, 27 a-a refrigerating drain pipe, 27 b-a freezing drain pipe, 28, 29, 30-a heat-insulating partition wall, 31-a control substrate, 32-an evaporation pan, 35-a refrigerating chamber, 39-a machine chamber, 40a refrigerating evaporator temperature sensor, 40 b-a refrigerating evaporator temperature sensor, 41-a refrigerating chamber temperature sensor (first load detecting unit), 42-freezing chamber temperature sensor (second load detecting means), 43-vegetable chamber temperature sensor, 50a, 50 b-outside-box radiator (heat radiating means), 50 c-condensation suppressing piping (heat radiating means), 51-dryer, 52-three-way valve (refrigerant control means), 53 a-refrigerating capillary (pressure reducing means), 53 b-refrigerating capillary (pressure reducing means), 54 a-refrigerating gas-liquid separator, 54 b-refrigerating gas-liquid separator, 55a, 55 b-heat exchanging portion, 56-check valve, 91-deodorizing means, 95a, 95 b-refrigerating chamber gasket (first sealing means), 96a, 96b, 96 c-freezing chamber gasket (second sealing means), 97-vegetable chamber gasket (third sealing means), 101-water conduit portion heater, 102-drain pipe upper heater, 103-drain pipe lower heater.

Detailed Description

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

Example 1

An embodiment of the refrigerator of the present invention will be described. First, a structure of a refrigerator according to an embodiment will be described with reference to fig. 1 to 5. Fig. 1 is a front view of a refrigerator of an embodiment, fig. 2 is a sectional view A-A of fig. 1, fig. 3 is a sectional view B-B of fig. 2, fig. 4 is a schematic view showing a wind path structure of the refrigerator of an embodiment, and fig. 5 is a schematic view showing a structure of a refrigerating cycle of the refrigerator of an embodiment. The heat insulating box 10 of the refrigerator 1 is opened to the front, and from above, the refrigerator includes a refrigerating chamber 2 (first refrigerating temperature zone chamber), an ice making chamber 3, an upper freezing chamber 4, a lower freezing chamber 5, and a vegetable chamber 6 (second refrigerating temperature zone chamber), which are juxtaposed in this order. Hereinafter, the ice making chamber 3, the upper layer freezing chamber 4, and the lower layer freezing chamber 5 are collectively referred to as a freezing chamber 7 (freezing temperature zone chamber).

The front opening of the refrigerating chamber 2 is opened and closed by rotary refrigerating chamber door leaves 2a, 2b divided left and right, and the front openings of the ice making chamber 3, the upper layer freezing chamber 4, the lower layer freezing chamber 5, and the vegetable chamber 6 are opened and closed by drawer-type ice making chamber door leaves 3a, upper layer freezing chamber door leaves 4a, lower layer freezing chamber door leaves 5a, and vegetable chamber door leaves 6a, respectively. Refrigerating chamber gaskets 95a and 95b (first sealing members) are provided as sealing members on the inner and outer peripheries of the refrigerating chamber door leaves 2a and 2b, freezing chamber gaskets 96a, 96b and 96c (second sealing members) are provided as sealing members on the inner and outer peripheries of the ice making chamber door leaf 3a, the upper freezing chamber door leaf 4a and the lower freezing chamber door leaf 5a, vegetable chamber gaskets 97 (third sealing members) are provided as sealing members on the inner and outer peripheries of the vegetable chamber door leaf 6a which is the door leaf of the vegetable chamber 6, and when the door leaves are closed, the sealing members come into contact with the front edge of the heat insulation box 10 to inhibit the circulation of air inside and outside the box. The circumferences of the refrigerating chamber gaskets 95a, 95b were 2271mm, 2441mm, respectively, and the total circumference of the refrigerating chamber gaskets 95a, 95b (circumference of the first sealing member) was 4712mm. The perimeters of the freezing chamber gaskets 96a, 96b, 96c are 976mm, 1416mm, 2087mm, respectively, and the total perimeter of the freezing chamber gaskets 96a, 96b, 96c (perimeter of the second sealing member) is 4209mm. Further, the perimeter of the vegetable room gasket 97 (the perimeter of the third sealing member) was 2107mm. The open/close states of the refrigerating chamber door leaves 2a, 2b, the ice making chamber door leaf 3a, the upper freezing chamber door leaf 4a, the lower freezing chamber door leaf 5a, and the vegetable chamber door leaf 6a are detected by a door leaf sensor, not shown, that detects the approaching state of each door leaf to the front edge of the heat insulation box 10.

In order to fix the refrigerator 1 and the door leaves 2a and 2b, door leaf hinges (not shown) are provided at upper and lower portions of the refrigerating chamber 2, and the upper door leaf hinges are covered with door leaf hinge covers 16. The door 2a is provided with an operation unit 99 for performing an operation of setting the temperature in the box.

Regarding the temperature of the refrigerating chamber 2 and the temperature of the freezing chamber 7, the user can select to maintain the temperature level via the operation portion 99. Specifically, the setting of the maintenance temperature levels of the refrigerating chamber 2 and the freezing chamber 7 can be set to three stages of "strong", "medium", and "weak", respectively, in which the refrigerating chamber 2 is maintained at about 2 ℃ under "strong", about 4 ℃ under "medium", about 6 ℃ under "weak", the freezing chamber 7 is maintained at about-22 ℃ under "strong", about-20 ℃ under "medium", and about-18 ℃ under "weak". The vegetable room 6 was maintained at about 7 ℃.

The refrigerator 1 has a width W of w=685 mm (see fig. 1), a depth D of d=738 mm (see fig. 2), a height H of h=1833 mm (see fig. 1), a refrigerating chamber height H _R of an opening of the heat insulating box 10 of H _R =787 mm, a freezing chamber height H _F of H _F =482 mm, and a vegetable chamber height H _V of H _V =334 mm (see fig. 2). The total rated capacity of the refrigerator compartment 2 (refrigerator compartment rated capacity) was 308L, and the rated capacity of the freezer compartment 7 (freezer compartment rated capacity) was 51.2% of the total rated capacity, the rated capacity of the freezer compartment 7 (freezer compartment rated capacity) was 180L, and the rated capacity of the vegetable compartment 6 (vegetable compartment rated capacity) was 29.9% of the total rated capacity (28% or more of the total rated capacity), and the rated capacity of the vegetable compartment 6 (vegetable compartment rated capacity) was 114L, and the total rated capacity was 18.9%, respectively, based on the total rated capacity of JISC9801-3:2015 of 602L.

As shown in fig. 2, the heat insulating box 10 formed by filling a foamed heat insulating material (for example, foamed polyurethane) between the outer box 10a and the inner box 10b is partitioned from the outside and the inside of the refrigerator 1. In the heat insulating box 10, a plurality of vacuum heat insulating materials 36 are installed between the outer box 10a made of steel plate and the inner box 10b made of synthetic resin in addition to the foamed heat insulating materials. The refrigerating compartment 2 and the upper-stage freezing compartment 4 and the ice making compartment 3 are partitioned by a heat insulating partition wall 28 (air flow shut-off means), and the lower-stage freezing compartment 5 and the vegetable compartment 6 are partitioned by a heat insulating partition wall 29. In addition, heat-insulating partition walls 30 are provided on the front surface sides of the respective storage compartments of the ice making compartment 3, the upper-stage freezing compartment 4, and the lower-stage freezing compartment 5 so as to prevent the circulation of air inside and outside the compartments through gaps between the door leaves 3a, 4a, and 5 a.

A plurality of door baskets 33a, 33b, 33c and a plurality of shelves 34a, 34b, 34c, 34d are provided inside the door leaves 2a, 2b of the refrigerator compartment 2 so as to define a plurality of storage spaces. The opening height (broken line in fig. 2) of the uppermost door basket 33a is set higher than the uppermost shelf 34 a. The freezing chamber 7 and the vegetable chamber 6 are provided with ice making chamber containers (not shown), upper-stage freezing chamber containers 4b, lower-stage freezing chamber containers 5b, and vegetable chamber containers 6b, which are integrally drawn out with the door leaves 3a, 4a, 5a, and 6a, respectively. The vegetable compartment container 6b is divided into two upper and lower layers, and a bottle accommodating space 6c capable of accommodating beverage bottles is provided in front of the lower layer side. The height dimension of the bottle housing space 6c is ensured to be 305mm or more so that 1.5L and 2L beverage bottles can be housed upright (315 mm in this embodiment). Further, bottles capable of containing beverages are known to users by means of catalogues, instructions for use, words, pictures, photographs, and videos of advertising media, and the like.

Above the heat-insulating partition wall 28, a chilled compartment 35 is provided, which can be set to a temperature lower than the temperature range of the refrigerating compartment 2. The user can select a set temperature of the chilled compartment 35 via the operation unit 99. Specifically, it can be set to any one of "temperature level 1" maintained at about 0to 3 ℃ in the refrigerating temperature zone and "temperature level 2" maintained at about-3 to 0 ℃ in the freezing temperature zone.

An ice-making water tank (not shown) is provided on the left side of the fresh air cooling chamber 35. The back of the ice-making water tank is provided with a water supply pump (not shown). Further, the ice-making water tank and the water supply pump are connected by a water supply pipe (not shown) from the water supply pump to the upper part of the ice-making tray (not shown) in the ice-making chamber 3 through the heat-insulating partition wall 28, and water can be supplied from the ice-making water tank to the ice-making tray by driving the water supply pump. The ice-making tray is connected to a deicing mechanism (not shown), and ice falls from the ice-making tray to the ice-making chamber container by operation of the deicing mechanism. When the automatic ice making function is turned ON, the user can select ON/OFF (ON/OFF) of the automatic ice making function via the operation unit 99, and the water in the ice making water tank is periodically supplied to the ice making tray by driving the water supply pump, and after a predetermined time has elapsed, the deicing mechanism automatically operates, so that ice drops to the ice making chamber container.

An evaporator chamber 8a for refrigeration is provided at a substantially rear portion of the refrigerating chamber 2, and an evaporator 14a for refrigeration (first evaporator) as a fin-tube heat exchanger is housed in the evaporator chamber 8a for refrigeration. A cooling fan 9a (first blower) is provided above the cooling evaporator 14 a. A refrigerator air blowing path 11 is provided at a substantially center of the back of the refrigerator 2 in the width direction, and a refrigerator discharge port 11a is provided at an upper portion of the refrigerator air blowing path 11, and the refrigerator discharge port 11a includes a directing means for directing blown air upward. In the refrigerator of the present embodiment, the opening of the refrigerator compartment outlet 11a is directed upward as the directing means of the refrigerator compartment outlet 11 a. The cooling air blown upward from the refrigerating compartment discharge port 11a flows along the ceiling surface of the refrigerating compartment 2 as indicated by an arrow in fig. 2 to reach the region in front of the refrigerating compartment 2, flows through gaps between the front side of the shelves 34a, 34b, 34c and the door leaf baskets 33a, 33b, 33c, enters the rear space of the refrigerating compartment 35 through the opening 92 (see fig. 3) provided in the left rear of the space between the shelf 34c and the shelf 34d, and returns to the refrigerating compartment 8a from the refrigerating compartment return air passages 15a, 15b, 15c (see fig. 3) provided in the lower front surface, the lower left side surface, and the lower right front surface of the refrigerating compartment 8a. In addition, a part of the air flowing through the space between the shelf 34c and the shelf 34d is returned to the refrigeration evaporator chamber 8a from the refrigerating chamber return air duct 15d (see fig. 3) provided in the right rear of the space between the shelf 34c and the shelf 34 d. A deodorizing member 91 (for example, a deodorizing member having an open hole structure) is provided in a part of the refrigerating compartment return air path 15c so as to be in contact with the air flowing through the refrigerating compartment 2.

A freezing evaporator chamber 8b is provided at a substantially rear portion of the freezing chamber 7, and a freezing evaporator 14b (second evaporator) as a fin-tube heat exchanger is housed in the freezing evaporator chamber 8 b. A freezing fan 9b is provided above the freezing evaporator 14 b. The freezing chamber 7 has a freezing chamber air-sending passage 12 at the back thereof, and the freezing chamber air-sending passage 12 in front of the freezing fan 9b (second fan) has a plurality of freezing chamber discharge ports 12a. A freezer return air duct 17 (see fig. 2 and 3) for returning the air sent to the freezer compartment 7 is provided in front of the lower part of the freezer evaporator chamber 8 b.

The vegetable room air-sending passage 13, which is an air passage to the vegetable room 6, is branched from the lower right side of the freezer air-sending passage 12, and passes through the heat-insulating partition wall 29. The vegetable room outlet 13a, which is the outlet of the vegetable room air blowing passage 13, is provided so as to be substantially equal to the height of the lower surface of the heat insulating partition wall 29 on the upper right side of the back of the vegetable room 6, and opens downward. The vegetable room air supply path 13 includes a vegetable room damper 19 (see fig. 3) as cooling control means for the vegetable room 6. A vegetable chamber return inlet 18a is provided in front of the left lower part of the heat-insulating partition wall 29 between the vegetable chamber 6 and the freezing chamber 7, and a flow path is formed to reach a vegetable chamber return outlet 18b provided in front of the lower part of the freezing evaporator chamber 8b via a vegetable chamber return air path 18 passing through the heat-insulating partition wall 29.

Next, the air path structure of the refrigerator of the present embodiment will be described with reference to fig. 4. By driving the cooling fan 9a, air having a low temperature by heat exchange with the cooling evaporator 14a is sent to the cooling chamber 2 through the cooling chamber air-sending passage 11 and the cooling chamber discharge port 11a, and the inside of the cooling chamber 2 is cooled. The air sent to the refrigerating chamber 2 is returned from the refrigerating chamber return air passages 15a, 15b, 15c, and 15d (see fig. 3) to the refrigerating evaporator chamber 8a. Hereinafter, the air passage from the refrigeration evaporator chamber 8a to the refrigeration evaporator chamber 8a through the refrigeration chamber 2 is referred to as a refrigeration air passage 111 (first air passage). By driving the freezing fan 9b, air having a low temperature by heat exchange with the freezing evaporator 14b is sent to the freezing chamber 7 through the freezing chamber air-sending passage 12 and the freezing chamber outlet 12a, and the inside of the freezing chamber 7 is cooled. The air sent to the freezing chamber 7 is returned to the freezing evaporator chamber 8b from the freezing chamber return air passage 17. When the vegetable compartment damper 19 is opened, a part of the cooling air flowing into the freezer compartment air-sending passage 12 flows through the vegetable compartment air-sending passage 13, reaches the vegetable compartment 6 through the vegetable compartment outlet 13a, and cools the interior of the vegetable compartment 6. The air sent to the vegetable room 6 flows through the vegetable room return air duct 18 and returns to the freezing evaporator chamber 8b. Hereinafter, the air passage from the freezing evaporator chamber 8b through the freezing chamber 7 to return to the freezing evaporator chamber 8b and the air passage from the freezing evaporator chamber 8b through the vegetable chamber 6 to return to the freezing evaporator chamber 8b are referred to as a frozen vegetable air passage 112 (second air passage).

In the refrigerator of the present embodiment, the cooling fan 9a is a centrifugal fan (backward fan) having a blade diameter of 100mm, and the freezing fan 9b is an axial fan (propeller fan) having a blade diameter of 110 mm. The centrifugal fan has a characteristic of turning the air sucked from the axial direction by 90 degrees to blow out in the radial direction. On the other hand, the axial flow fan has a characteristic of blowing out air pressure sucked from the axial direction in the axial direction. Therefore, the centrifugal fan is excellent in the attachment property in the air passage for turning the flow sucked in the axial direction to 90 degrees, and the axial fan is excellent in the attachment property in the air passage for blowing the flow sucked in the axial direction. Therefore, the refrigerating fan 9a is configured to blow out the air sucked from the front side to the refrigerating compartment air-sending passage 11 in the upward direction by turning the air sucked from the front side by 90 degrees, and therefore a rear fan serving as a centrifugal fan is employed as the freezing fan 9b, and the refrigerating compartment air-sending passage 12 in the front side by blowing out the air sucked from the rear side is configured to use a propeller fan serving as an axial fan, so that a refrigerator having high space efficiency is obtained.

As shown in fig. 2 and 3, the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6 are provided with a refrigerator compartment temperature sensor 41 (first load detecting means), a freezer compartment temperature sensor 42 (second load detecting means), and a vegetable compartment temperature sensor 43 on the back side in the cabinet, and detect temperatures of the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6, respectively. The refrigerating evaporator 14a has a refrigerating evaporator temperature sensor 40a at an upper portion thereof, and the freezing evaporator 14b has a freezing evaporator temperature sensor 40b at an upper portion thereof, so as to detect temperatures of the refrigerating evaporator 14a and the freezing evaporator 14 b. The door hinge cover 16 of the ceiling portion of the refrigerator 1 is provided with an outside air temperature/humidity sensor 37 for detecting the temperature and humidity of outside air (outside air), and the door 2a, 2b, 3a, 4a, 5a, and 6a are provided with door sensors (not shown) for detecting the open/closed states, respectively.

A defrosting heater 21 for heating the freezing evaporator 14b is provided at the lower portion of the freezing evaporator chamber 8 b. The defrosting heater 21 is an electric heater of, for example, 50W to 200W, and in this embodiment, a radiation heater of 150W is provided. The defrost water (melt water) generated when the refrigerator evaporator 14b is defrosted flows down to the water guide pipe 23b provided at the lower portion of the refrigerator evaporator chamber 8b, reaches the machine chamber 39 provided at the lower portion of the rear (back surface side) of the refrigerator 1 via the drain port 22b and the refrigerator drain pipe 27b, and is discharged to the evaporation pan 32 provided at the upper portion of the compressor 24 in the machine chamber 39.

The defrosting method of the refrigeration evaporator 14a will be described later, but defrosting water generated when the refrigeration evaporator 14a is defrosted flows down to the water guide pipe 23a provided at the lower portion of the refrigeration evaporator chamber 8a, and is discharged to the evaporation pan 32 provided at the upper portion of the compressor 24 via the water discharge port 22a and the refrigeration drain pipe 27 a.

The machine chamber 39 includes an external radiator 50a and an external fan 26 as fin-tube heat exchangers, together with the compressor 24 and the evaporating dish 32. By driving the outside fan 26, air flows through the compressor 24, the outside radiator 50a, and the evaporation pan 32, heat dissipation from the compressor 24 and the outside radiator 50a is promoted, energy saving performance is improved, and by ventilation to the evaporation pan 32, evaporation of defrost water stored in the evaporation pan 32 is promoted, overflow is suppressed, and reliability is improved.

As shown in fig. 3, the water guide pipe 23a is provided with a water guide pipe heater 101 for melting defrost water frozen in the water guide pipe 23 a. The drain pipe 27a for refrigeration includes a drain pipe upper heater 102 and a drain pipe lower heater 103. In the present embodiment, the power of each of the drain pipe heater 101, the drain pipe upper heater 102, and the drain pipe lower heater 103 is lower than that of the defrost heater 21, and in this embodiment, the drain pipe heater 101 is set to 6W, the drain pipe upper heater 102 is set to 3W, and the drain pipe lower heater 103 is set to 1W.

Here, when the cooling fan 9a is driven, the return air from the cooling chamber 2 flows downward toward the water guide pipe 23a through the cooling chamber return port 15b provided in the upper right of the cooling evaporator chamber 8a, and the water guide pipe 23a is heated to raise the temperature. This can reduce the heating amount of the drain heater 101 for melting the defrost water frozen in the drain pipe 23a, thereby improving the energy saving performance.

The lower portion of the drain pipe 27a is closer to the outer casing 10a than the freezing chamber 7 and the freezing evaporator chamber 8 b. This can reduce the heating amount of the drain lower heater 103 for melting the defrost water frozen in the drain pipe 27a, and improve the energy saving performance.

A control board 31 is disposed in a ceiling portion (see fig. 2) of the refrigerator 1, and the control board 31 is mounted with a memory such as CPU, ROM, RAM, an interface circuit, and the like, which are part of a control device. The control board 31 is connected to the refrigerator temperature sensor 41, the freezer temperature sensor 42, the vegetable room temperature sensor 43, the evaporator temperature sensors 40a, 40b, and the like, and the CPU performs control of the compressor 24, the refrigerating fan 9a, the freezing fan 9b ON/OFF, the rotation speed control, the defrost heater 21, the water guide pipe heater 101, the drain pipe upper heater 102, the drain pipe lower heater 103, the three-way valve 52 described later, and the like based ON the output values thereof, the setting of the operation unit 99, and the programs recorded in the ROM in advance.

Fig. 5 is a refrigeration cycle (refrigerant flow path) of the refrigerator of embodiment 1. The refrigerator 1 of the present embodiment includes: compressor 24 (displacement 9.2 cc); an outside radiator 50a and a wall surface heat radiation pipe 50b for radiating the refrigerant; a condensation suppressing pipe 50c (the outside radiator 50a, the outside radiator 50b, and the condensation suppressing pipe 50c are referred to as a heat radiating unit) for suppressing condensation on the front edge portions of the heat insulating partition walls 28, 29, and 30; a three-way valve 52 as a refrigerant flow control unit; a refrigerating capillary 53a and a freezing capillary 53b as a decompression means for decompressing the refrigerant; and a refrigerating evaporator 14a and a freezing evaporator 14b for absorbing heat in the tank by exchanging heat between the refrigerant and air in the tank. A dryer 51 for removing moisture in the refrigeration cycle is provided upstream of the three-way valve 52, and a refrigeration gas-liquid separator 54a and a refrigeration gas-liquid separator 54b for preventing liquid refrigerant from flowing into the compressor 24 are provided downstream of the refrigeration evaporator 14a and downstream of the refrigeration evaporator 14b, respectively. A check valve 56 is further provided downstream of the refrigeration gas-liquid separator 54b. These components are connected by a refrigerant pipe, thereby constituting a refrigeration cycle. In the refrigerator of the present embodiment, the temperatures of the refrigerating evaporator 14a and the freezing evaporator 14b are adjusted by the rotational speeds of the compressor 24, the refrigerating fan 9a, and the freezing fan 9b, and therefore, the compressor 24, the refrigerating fan 9a, and the freezing fan 9b are referred to as an evaporator temperature adjusting means. In addition, as the refrigerant, isobutane as a flammable refrigerant was used, and the refrigerant amount was 88g.

The three-way valve 52 is a refrigerant flow control valve as follows: the device is provided with an outflow port 52a and an outflow port 52b, and is provided with: a state 1 (cooling mode) in which the outflow port 52a is opened, the outflow port 52b is closed, and the refrigerant flows into the cooling capillary 53 a; a state 2 (freezing mode) in which the outflow port 52a is closed, the outflow port 52b is opened, and the refrigerant flows into the freezing capillary 53b side; and a state 3 (full-closed mode) in which both the outflow ports 52a and 52b are closed.

When the three-way valve 52 is controlled to be in state 1 (refrigeration mode), the refrigerant discharged from the compressor 24 flows through the outside radiator 50a, the outside radiator 50b, and the condensation suppressing pipe 50c to dissipate heat, and reaches the three-way valve 52 via the dryer 51. Since the three-way valve 52 is in state 1 (the outflow port 52a is opened and the outflow port 52b is closed), the refrigerant is then circulated through the refrigerating capillary 53a and depressurized, reaches the refrigerating evaporator 14a, and exchanges heat with the return air in the refrigerating chamber 2. The refrigerant leaving 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 through the capillary tube 53a, and returns to the compressor 24.

When the three-way valve 52 is controlled to be in state 2 (the freeze mode), the refrigerant discharged from the compressor 24 flows through the outside radiator 50a, the outside radiator 50b, and the condensation suppressing pipe 50c to dissipate heat, and reaches the three-way valve 52 via the dryer 51. Since the three-way valve 52 is in the state 2 (the outflow port 52a is closed and the outflow port 52b is opened), the refrigerant is then circulated through the freezing capillary 53b, depressurized, cooled, and heat-exchanged between the freezing evaporator 14b and the return air of the freezing chamber 7 and the return air of the vegetable chamber 6 (when the vegetable chamber barrier 19 is opened). The refrigerant leaving the refrigeration evaporator 14b flows through the refrigeration gas-liquid separator 54b at the contact portion 57b with the capillary tube 53b, exchanges heat with the refrigerant flowing through 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), the refrigerant in the refrigeration evaporator 14a or the refrigerant in the freezing evaporator 14b is collected to the heat radiation unit side because the refrigerant is not supplied from the refrigeration capillary 53a or the freezing capillary 53b when the compressor 24 is driven (details will be described later).

The refrigerator of the present embodiment cools each storage chamber in the refrigerator 1 by appropriately performing the following operations: the three-way valve 52 is controlled to be in the state 1 (refrigeration mode), the compressor 24 is driven, the refrigeration fan 9a is driven, and the freezing fan 9b is stopped, so that the "refrigeration operation" of the refrigerating chamber 2 is cooled; by controlling the three-way valve 52 to the state 2 (freezing mode), setting the compressor 24 to the driving state, setting the vegetable room barrier 19 to the open state, setting the cooling fan 9a to the driving state or the stopped state, and setting the freezing fan 9b to the driving state, the "frozen vegetable operation" of the freezing chamber 7 and the vegetable room 6 is cooled; by controlling the three-way valve 52 to the state 2 (freezing mode), setting the compressor 24 to the driving state, setting the vegetable room barrier 19 to the closed state, setting the cooling fan 9a to the driving state or the stopped state, and setting the freezing fan 9b to the driving state, the "freezing operation" of the freezing chamber 7 is cooled; the three-way valve 52 is controlled to be in the state 3 (full-closed mode), and the compressor 24 is driven, so that the refrigerant in the refrigeration evaporator 14a or the refrigerant in the freezing evaporator 14b is recovered to the heat radiation unit side; the three-way valve 52 is set to the state 3 (full-closed mode), the compressor 24 is set to the stopped state, the cooling fan 9a is set to the stopped state, and the freezing fan 9b is set to the stopped state "operation stop"; the three-way valve 52 is controlled to be in the state 2 (freezing mode) and the compressor 24 is controlled to be in the driving state, or the three-way valve 52 is controlled to be in the state 3 (full-closed mode) and the compressor 24 is controlled to be in the stopped state, and the refrigerating fan is set to be in the driving state, so that the refrigerating chamber 2 is cooled by the frost growing on the surface of the refrigerating evaporator 14a and the cold heat of the evaporator itself, and the defrosting of the refrigerating evaporator 14a is performed; the three-way valve 52 is set to the state 3 (full-closed mode), the compressor 24 is set to the stopped state, the cooling fan 9a is set to the driven state or the stopped state, the freezing fan 9b is set to the stopped state, and the defrosting heater 21 is set to the energized state, so that the "defrosting operation of the freezing evaporator" of the freezing evaporator 14b is performed.

The interval (defrosting interval) at which the defrosting operation of the evaporator for freezing is performed may be changed between the longest 96 hours (longest defrosting interval) and the shortest 12 hours (shortest defrosting interval). Specifically, the defrosting interval is determined based on the outside air temperature and humidity detected by the outside air temperature and humidity sensor 37, the number of times the door leaves 3a, 4a, 5a, 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 detected by the freezing evaporator temperature sensor 40b, and the higher the outside air temperature, the higher the number of times the door leaves of the freezing chamber are opened and closed, and the lower the minimum reaching temperature of the freezing evaporator temperature during the freezing operation and the frozen vegetable operation, the shorter the interval. By changing the intervals of the defrosting operation of the freezing evaporator in this way, the defrosting operation of the freezing evaporator can be performed at an appropriate timing when frost grows in the freezing evaporator 14b, and therefore, excessive growth of frost can be suppressed, and the heat exchange efficiency of the freezing evaporator can be greatly reduced, and good practical cooling performance can be exhibited. In addition, by setting the longest defrosting interval, the reliable defrosting operation of the freezing evaporator can be performed periodically. This can suppress the unexpected growth of frost on the wall surface of the refrigeration evaporator chamber 8b other than the refrigeration evaporator 14b, and improve the reliability. In addition, since the freezing chamber 7 cannot be cooled during the defrosting operation of the freezing evaporator, the temperature of the freezing chamber 7 increases. In the refrigerator of the present embodiment, by providing the shortest defrosting interval, it is possible to prevent the defrosting interval from being too short, and the temperature of the freezing compartment 7 does not rise frequently due to the defrosting operation, thereby making the refrigerator less prone to the problem of thawing frozen foods.

When the refrigerant in the refrigeration evaporator 14a is collected toward the heat radiation unit, the refrigeration fan 9a is driven, and when the refrigerant in the freezing evaporator 14b is collected toward the heat radiation unit, the freezing fan 9b is driven, so that the refrigerating chamber 2 and the freezing chamber 7 are cooled even in the refrigerant collection operation (details will be described later). Therefore, the "cooling operation" in which the cooling of the refrigerating chamber 2 is performed and the refrigerant recovery operation for recovering the refrigerant in the refrigerating evaporator 14a are collectively referred to as "refrigerating chamber cooling operation", and the "frozen vegetable operation", "freezing operation", in which the cooling of the freezing chamber 7 is performed, and the refrigerant recovery operation for recovering the refrigerant in the freezing evaporator 14b are collectively referred to as "freezing chamber cooling operation".

Fig. 6 is a diagram showing an evaporator of the refrigerator of the present embodiment, in which fig. 6 (a) is a refrigeration evaporator 14a, and fig. 6 (b) is a freezing evaporator. As shown in fig. 6 (a), the refrigeration evaporator 14a is a fin-tube heat exchanger in which aluminum fins 98a are attached to an aluminum refrigerant tube 97a. The refrigerant depressurized by the refrigerating capillary tube 53a (see fig. 5) to be low-temperature and low-pressure circulates in the refrigerant tube 97a, and exchanges heat with the return air from the refrigerating chamber 2 (see fig. 2 or 3) flowing from the front lower portion of the refrigerating evaporator 14a via the fin 98a and the surface of the refrigerant tube 97a. The fin 98a is divided into three layers in the height direction, and refrigerant tubes 97a of two front and rear rows are provided in each layer. The refrigerant flows into the refrigerant tube 97a at the rear of the upper part of the refrigeration evaporator 14a, and flows downward toward the rear of the first layer of the fins 98a at the right side of the refrigeration evaporator 14 a. Then, the flow is conducted in the order of the second layer rear, the third layer front, the second layer front, and the first layer front, and flows out from the right side of the first layer. A refrigeration gas-liquid separator 54a connected to the refrigerant pipe 97a is provided on the right side of the refrigeration evaporator 14a, and separates the liquid refrigerant and the gas refrigerant. The refrigerant tube in the rear of the upper part of the refrigeration evaporator 14a is attached with a not-shown sensor holder to which the refrigeration evaporator temperature sensor 40a is attached. In the refrigeration evaporator 14a, a portion (fin installation portion) where the fins 98a that perform main heat exchange are provided has a width W _Revp =300 mm, a depth D _Revp =60 mm, a height H _Revp =88 mm, and an occupied volume (refrigeration evaporator volume) V _Revp =1.486L of the fin installation portion. In addition, the fin pitch Pf _Revp =3 mm. The surface area (air-side heat transfer area) a _Revp of the fins 98a of the fin mounting portion and the surface area (air-side heat transfer area) a _Revp of the refrigerant tube 97a, which is in contact with air, is 0.993m ².

Fig. 6 (b) shows the refrigeration evaporator 14b, which is a fin-tube heat exchanger in which aluminum fins 98b are attached to an aluminum refrigerant tube 97b. The refrigerant depressurized by the freezing capillary tube 53b (see fig. 5) to be low-temperature and low-pressure circulates in the refrigerant tube 97b, and exchanges heat with the return air (see fig. 2 or 3) from the freezing chamber 7 and the vegetable chamber 6 flowing from the front lower part of the freezing evaporator 14b via the fin 98b and the surface of the refrigerant tube 97b. The fin 98b is divided into five layers in the height direction of the refrigeration evaporator 14b, and refrigerant tubes 97b in two rows, one front and one rear, are provided in each layer. The refrigerant flows into the refrigerant tube 97b in front of the upper portion of the refrigeration evaporator 14a and flows into front of the fifth layer of the fins 98 a. Then, the flow is made in the order of the fourth layer front, the third layer front, the second layer front, the first layer rear, the second layer rear, the third layer rear, the fourth layer rear, and the fifth layer rear, and flows out from the upper left of the fifth layer rear. A refrigeration gas-liquid separator 54b connected to the refrigerant pipe 97b is provided at the upper left side of the refrigeration evaporator 14b so as to be inclined at a predetermined angle (15 degrees) with respect to the plumb line, and separates the liquid refrigerant and the gas refrigerant. A refrigerant tube in front of the upper portion of the refrigeration evaporator 14a is attached with a refrigeration evaporator temperature sensor 40b via a sensor holder, not shown. In the evaporator 14b for freezing, the width of the portion (fin installation portion) where the fins 98b for main heat exchange are provided is W _Fevp 1=345 mm, the fifth layer is W _Fevp 2=300 mm, the depth D _Fevp =60 mm, The heights H _evp1 to fourth layers are each equal to 118mm, and the heights H _evp1 to 30mm of the fifth layer. The occupied volume (evaporator volume for freezing) V _Fevp = 2.983L of the fin installation portion determined by these is 3% or less of the rated capacity 180L of the freezing chamber 7. By setting the volume of the evaporator for freezing to 3% or less of the rated capacity of the freezing chamber 7 in this way, the rated capacity of the freezing chamber 7 can be increased to 28% or more of the total rated capacity. Further, the fin pitch Pf _Fevp =5 mm, and the surface areas (air-side heat transfer areas) a _Fevp＝1.146m² of the fins 98b of the fin installation portion and the refrigerant tube 97b in contact with air.

The air-side heat transfer areas per unit volume of the refrigeration evaporator 14a and the freezing evaporator 14b shown in fig. 6 are a _Revp/V_Revp＝0.673m²/L,A_Fevp/V_Fevp＝0.384m²/L and 0.25m ²/L to 0.96m ²/L, respectively. Generally, frost grows on the air-side heat transfer surface of the evaporator, and therefore, if the air-side heat transfer area is increased with respect to the volume of the evaporator, the flow path is easily blocked when frost grows. Therefore, the evaporator is likely to cause a decrease in heat exchange performance when the frost grows more, and has a high heat exchange performance when the frost grows less. On the other hand, if the air-side heat transfer area is reduced with respect to the evaporator volume, even if frost grows, the flow path is less likely to be blocked by the frost, and the heat exchange performance is likely to be maintained. Therefore, in the refrigerator of the present embodiment, the performance of the case where the growth of frost is large and the case where the growth of frost is small can be achieved by setting the air-side heat transfer area per unit volume of the refrigerating evaporator 14a and the freezing evaporator 14b to 0.25m ²/L or more and 0.96m ²/L or less.

The structure of the refrigerator of the present embodiment is described above, and next, control of the refrigerator of the present embodiment is described. Fig. 7 is a flowchart showing control in the normal operation state of the refrigerator of the present embodiment. Fig. 8 is a flowchart showing control in a high load state of the refrigerator of the present embodiment. Fig. 9 is a timing chart showing control in the normal operation state of the refrigerator of the present embodiment. Fig. 10 is a timing chart showing control in a high load state of the refrigerator of the present embodiment.

As shown in fig. 7, the refrigerator of the present embodiment starts operation (startup) by turning on the power supply, cooling each storage chamber of the refrigerator 1. In a normal operation state (normal operation mode) in which there is no load fluctuation due to a user opening and closing each storage compartment door or a change in the temperature environment around the refrigerator, the operation mode is basically repeated (hereinafter, referred to as a steady cooling operation). In fig. 7, the control process from the time of turning on the power supply to the time of reaching the steady cooling operation is omitted.

In the steady cooling operation, a fixed operation mode (operation cycle) is repeatedly performed, and here, control from the start of the cooling operation as the operation mode for cooling the refrigerating chamber 2 will be described. The cooling operation is started by: the three-way valve 52 is set to state 1 (refrigeration mode), the compressor 24 is driven at speed 1 (800 min ^-1), the refrigeration fan 9a is driven at speed 2 (1500 min ^-1), the refrigeration fan 9b is stopped, and the vegetable room barrier 19 is closed (step S101). Next, it is determined whether or not the load in the tank is high (step S102). In the refrigerator of the present embodiment, step S102 is established when the freezing chamber temperature T _F detected by the freezing chamber temperature sensor 42 is the high load determination temperature T _{F_high} (= -10 ℃) or higher (T _F≥T_{F_high}), or the refrigerating chamber temperature T _R detected by the refrigerating chamber temperature sensor 41 is the high load determination temperature T _{R_high} (=10 ℃) or higher (T _R≥T_{R_high}). The control when step S102 is established will be described later.

At this time, when the time average temperature of the refrigeration evaporator 14a during the refrigeration operation is T _{Revp_ave}, the maintenance temperature of the refrigeration chamber 2 is T _{F_keep}, the maintenance temperature of the freezing chamber 7 is T _{F_keep}, the difference between the refrigeration chamber 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 coefficient of performance of the refrigeration cycle with respect to the evaporator temperature is COP _th, the compressor 24 and the refrigeration fan 9a are selected so as to satisfy T_{Revp_ave}≥0.5×(T_{R_keep}+T_{F_keep})、d²(COP_th)/dT_{Revp_ave} ²-d²(ΔT^-1)/dT_{Revp_ave} ²≥0.

If step S102 is not satisfied (No), then it is determined whether or not the cooling operation end condition is satisfied (step S103). In the refrigerator of the present embodiment, when the refrigerating room temperature T _R detected by the refrigerating room temperature sensor 41 is equal to or lower than the refrigerating operation end temperature T _Roff (=2.5 ℃) and (T _R≤T_Roff), step S103 is established. If step S103 is not satisfied (No), the routine returns to the determination of step S102.

If step S103 is satisfied (Yes), it is then determined whether or not the frozen vegetable operation start condition is satisfied (step S104). In the refrigerator of the present embodiment, when the freezing chamber temperature T _F detected by the freezing chamber temperature sensor 42 is equal to or higher than the frozen vegetable operation start temperature T _{F_on} (= -18 ℃) and (T _F≥T_{F_on}), step S104 is established.

When step S104 is satisfied (when not satisfied (No) will be described later), then the three-way valve 52 is set to state 3 (fully closed mode) while maintaining the driving rotational speed of the compressor 24, and the refrigerant recovery operation is performed to recover the refrigerant in the refrigeration evaporator 14a to the heat radiation unit side (step S105). At this time, the cooling fan 9a continues to be driven, and the cooling of the refrigerating chamber 2 is also performed during the refrigerant recovery operation.

Next, it is determined whether or not to perform the defrosting operation of the refrigerating evaporator (step S106). In the refrigerator of the present embodiment, when the setting of the cooling chamber 35 provided in the lower portion of the refrigerating chamber 2 is selected to maintain the "temperature level 1" of about 0 to 3 ℃ of the refrigerating temperature zone, step S106 is established (Yes), and when the setting of the "temperature level 2" of about-3 to 0 ℃ of the freezing temperature zone is selected to maintain the refrigerating temperature zone, step S106 is not established (No). If step S106 is satisfied (Yes), the cooling fan 9a is set to a speed of 1 (900 min ^-1), the defrosting operation of the cooling evaporator is started (step S107), and if step S106 is not satisfied (No), the cooling fan 9a is stopped (step S108).

Next, the frozen vegetable operation is started (step S109). The frozen vegetable operation was performed in the following state: the three-way valve 52 was set to state 2 (freezing mode), the compressor 24 was driven at speed 2 (1400 min ^-1), the freezing fan 9b was driven at speed 1 (1200 min ^-1), and the vegetable room barrier 19 was opened.

Next, it is determined whether or not the load in the tank is high (step S110). In the refrigerator of the present embodiment, when the freezing chamber temperature T _F detected by the freezing chamber temperature sensor 42 is the high load determination temperature T _{F_high} (= -10 ℃) or higher (T _F≥T_{F_high}), or the refrigerating chamber temperature T _R detected by the refrigerating chamber temperature sensor 41 is the high load determination temperature T _{R_high} (=10 ℃) or higher (T _R≥T_{R_high}), step S110 is established (determination similar to step S102). The control when step S110 is established will be described later.

If step S110 is not satisfied (No), it is then determined whether or not the vegetable room cooling completion condition is satisfied (step S111). In the refrigerator of the present embodiment, when the vegetable room temperature T _V detected by the vegetable room temperature sensor 43 is equal to or lower than the vegetable room cooling end temperature T _{V_off} (=4 ℃) and is equal to or lower than (T _V≤T_{V_off}), step S111 is established. If step S111 is satisfied (Yes), the vegetable compartment damper 19 is closed, and the frozen vegetable operation is ended, and the operation is switched to the freezing operation for cooling the freezing compartment 7.

If step S111 is not satisfied (No), then it is determined whether or not the defrosting operation end condition of the refrigeration evaporator is satisfied (step S113). The defrosting operation end condition of the refrigeration evaporator is established when the temperature T _{R_evp} of the refrigeration evaporator is equal to or higher than the defrosting operation end temperature T _{RD_off} (=2 ℃) of the refrigeration evaporator (T _{R_evp}≥T_{RD_off}). If step S113 is satisfied (Yes), the cooling fan 9a is stopped (step S114), and the "cooling evaporator defrosting operation" is ended.

If step S113 is not satisfied (No), then it is determined whether or not the cooling operation end condition is satisfied (step S115). In the refrigerator of the present embodiment, when the vegetable room barrier 19 is in the closed state and the freezing chamber temperature T _F is equal to or lower than the freezing operation end temperature T _{F_off} (= -22.5 ℃) and (T _F≥T_{F_off}), step S115 is established. If step S115 is not satisfied (No), the process returns to the determination of step S110.

If step S115 is satisfied, it is then determined whether or not the cooling operation start condition is satisfied (step S116). In the refrigerator of the present embodiment, when the refrigerating room temperature T _R detected by the refrigerating room temperature sensor 41 is equal to or higher than the refrigerating operation start temperature T _{R_on} (=5.5 ℃) and (T _R≥T_{R_on}), step S116 is established.

When step S116 is satisfied (when No is satisfied, described later), the three-way valve 52 is set to state 3 (fully closed mode) while maintaining the driving rotational speed of the compressor 24, and the refrigerant recovery operation for recovering the refrigerant in the refrigeration evaporator 14b to the heat radiation unit side is performed (step S117). At this time, the cooling fan 9b continues to be driven, and the freezing chamber 7 is cooled during the refrigerant recovery operation.

If step S104 is not satisfied (No), then it is determined whether or not to perform the defrosting operation of the refrigeration evaporator (step S201). In the refrigerator of the present embodiment, when the setting of the cooling chamber 35 provided in the lower portion of the refrigerating chamber 2 is selected to maintain the "temperature level 1" of about 0 to 3 ℃ in the refrigerating temperature zone, step S106 is established (Yes), and when the setting of the "temperature level 2" of about-3 to 0 ℃ in the freezing temperature zone is selected to maintain the "temperature level 2", step S106 is not established (No) (the same judgment as step S106). If step S201 is true (Yes), the cooling fan 9a is set to a speed of 1 (900 min ^-1), the defrosting operation of the cooling evaporator is started (step S202), and if step S106 is not true (No), the cooling fan 9a is stopped (step S203), the three-way valve 52 is set to a state of 3 (full-closed mode), the compressor 24 is stopped, and the freezing fan 9b is stopped (step S118). If step S116 is not satisfied (No), the three-way valve 52 is set to state 3 (full-closed mode), the compressor 24 is stopped, and the cooling fan 9b is stopped (step S118).

Next, it is determined whether or not the load in the tank is high (step S119). In the refrigerator of the present embodiment, when the freezing chamber temperature T _F detected by the freezing chamber temperature sensor 42 is the high load determination temperature T _{F_high} (= -10 ℃) or higher (T _F≥T_{F_high}), or the refrigerating chamber temperature T _R detected by the refrigerating chamber temperature sensor 41 is the high load determination temperature T _{R_high} (=10 ℃) or higher (T _R≥T_{R_high}), step S119 is established (determination similar to steps S102 and 110). The control when step S119 is established will be described later.

If step S119 is not satisfied (No), it is then determined whether or not the defrosting operation end condition of the refrigeration evaporator is satisfied (step S120). The defrosting operation end condition of the refrigeration evaporator is established 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 ℃) and is equal to or higher than (T _{R_evp}≥T_{RD_off}) (determination similar to step S113). If step S120 is satisfied (Yes), the cooling fan 9a is stopped (step S121), and the "cooling evaporator defrosting operation" is ended.

If step S120 is not satisfied (No), then it is determined whether or not the frozen vegetable operation start condition is satisfied (step S122). In the refrigerator of the present embodiment, when the freezing chamber temperature T _F detected by the freezing chamber temperature sensor 42 is equal to or higher than the frozen vegetable operation start temperature T _{F_on} (= -18 ℃) and is equal to or higher than (T _F≥T_{F_on}), step S122 is established (the same determination as step S104). If step S122 is true (Yes), it is then determined whether or not the refrigerant recovery operation is to be performed (step S123). In the refrigerator of the present embodiment, step S123 is established when the operation before stopping the compressor 24 based on step S118 is the cooling operation. If step S123 is satisfied (Yes), the three-way valve 52 is set to state 3 (full-closed mode), the compressor 24 is driven at the rotation speed in the previous refrigerating operation, the refrigerant recovery operation for recovering the refrigerant in the refrigerating evaporator 14a to the heat radiation unit side is performed (step S124), and the vegetable freezing operation is started (step S109). If step S123 is not satisfied (No), the refrigerant recovery operation is not performed, and the vegetable freezing operation is started (step S109).

If step S122 is not satisfied (No), then it is determined whether or not the cooling operation start condition is satisfied (step S125). In the refrigerator of the present embodiment, when the refrigerating room temperature T _R detected by the refrigerating room temperature sensor 41 is equal to or higher than the refrigerating operation start temperature T _{R_on} (=5.5 ℃) and (T _R≥T_{R_on}), step S116 is established (the same judgment as step S116).

If step S125 is satisfied, it is then determined whether or not to perform the refrigerant recovery operation (step S126). In the refrigerator of the present embodiment, step S126 is established when the operation before stopping the compressor 24 based on step S118 is the cooling operation. If step S126 is satisfied (Yes), the three-way valve 52 is set to state 3 (full-closed mode), the compressor 24 is driven at the rotation speed in the previous cooling operation, the refrigerant recovery operation for recovering the refrigerant in the cooling evaporator 14b to the heat radiation unit side is performed (step S127), and the cooling operation is started (step S101). If step S126 is not satisfied (No), the refrigerant recovery operation is not performed, and the cooling operation is started (step S101).

In the above description, the refrigeration operation start temperature T _{R_on} (=5.5 ℃) and the refrigeration operation end temperature T _{R_off} (=2.5 ℃) and the frozen vegetable operation start temperature T _{F_on} (= -18 ℃) and the frozen operation end temperature T _{F_off} (= -22.5 ℃) are examples in which the maintenance temperature level of the refrigeration compartment 2 is set to "medium", and the maintenance temperature level of the freezing compartment 7 is set to "medium", and may be changed according to the set maintenance temperature level.

Next, control when the inside of the refrigerator 1 is under a high load will be described with reference to fig. 8. In the case where steps S102, S110, and S119 in fig. 7 determine that the refrigerator 1 is under a high load in the refrigerator (Yes in each step), the control is shifted to the control shown in fig. 8. When it is determined that the load in the box is high, then, a determination is made as to whether or not the refrigerating chamber 2 is high (step S301). If the refrigerating chamber 2 is not under a high load, step S301 is No, and it is then determined whether or not the refrigerant recovery operation is performed (step S501).

In the refrigerator of the present embodiment, when the operation at the time when any of steps S102, S110, and S119 in fig. 7 is established is the cooling operation, step S501 is established. If step S501 is satisfied (Yes), the three-way valve 52 is set to state 3 (full-closed mode), the compressor 24 is driven at the rotation speed in the previous refrigerating operation, the refrigerant recovery operation for recovering the refrigerant in the refrigerating evaporator 14a to the heat radiation unit side is performed (step S502), and then the "high-load mode frozen vegetable/frozen operation" is selected (step S503). If step S501 is not satisfied (No), the "high-load mode frozen vegetable/frozen operation" is selected without performing the refrigerant recovery operation (step S503). In the refrigerator of the present embodiment, when the "high-load mode frozen vegetable/frozen operation" is selected, the compressor 24 is set to a speed 4 (3600 min ^-1), and the freezing fan 9b is set to a speed 2 (2000 min ^-1) as the rotational speed at the time of performing the frozen vegetable operation or the frozen operation. The rotation speeds of the compressor 24 and the cooling fan 9a when the cooling operation and the defrosting operation of the cooling evaporator are performed are selected to be the same as those in the normal operation mode.

If the freezing chamber 7 is under a high load (Yes in step S301) and the refrigerating chamber 2 is not under a high load, no in step S302, it is determined whether or not the refrigerant recovery operation is performed (step S401).

In the refrigerator of the present embodiment, when the operation at the time when any one of steps S102, S110, and S119 in fig. 7 is established is the frozen vegetable operation or the freezing operation, step S401 is established. If step S401 is satisfied (Yes), the three-way valve 52 is set to state 3 (full-closed mode), the compressor 24 is driven at the previous frozen vegetable operation or at the rotation speed in the freezing operation, the refrigerant recovery operation for recovering the refrigerant in the freezing evaporator 14b to the heat radiation unit side is performed (step S402), and then the "high load mode cooling operation" is selected (step S403). If step S401 is not satisfied (No), the "high-load mode cooling operation" is selected without performing the refrigerant recovery operation (step S403). In the refrigerator of the present embodiment, when the "high-load mode cooling operation" is selected, the speed of the compressor 24 is set to 3 (2500 min ^-1), and the rotational speed of the cooling fan 9a is set to 3 (2000 min ^-1). The rotation speeds of the compressor 24, the cooling fan 9a, and the freezing fan 9b when the frozen vegetable operation, the freezing operation, and the defrosting operation of the refrigerating evaporator are performed are selected to be the same as those in the normal operation mode.

When both the freezing compartment 7 and the refrigerating compartment 2 are under high load (Yes in step S301 and step S302), it is then determined whether or not the refrigerant recovery operation is performed (step S303). In the refrigerator of the present embodiment, when the operation at the time when any one of steps S102, S110, and S119 in fig. 7 is established is the cooling operation, step S303 is established. If step S303 is satisfied (Yes), the three-way valve 52 is set to state 3 (full-closed mode), the compressor 24 is driven at the rotation speed in the previous cooling operation, the refrigerant recovery operation for recovering the refrigerant in the cooling evaporator 14a to the heat radiation unit side is performed (step S304), and then the "overload mode" is selected (step S305). In the refrigerator of the present embodiment, when the "overload mode" is selected, the compressor 24 is set to a speed 3 (2500 min ^-1), the cooling fan 9a is set to a speed 3 (2000 min ^-1), the compressor 24 is set to a speed 4 (3600 min ^-1), and the cooling fan 9b is set to a speed 2 (2000 min ^-1) as the rotational speed at the time of performing the frozen vegetable operation or the freezing operation. The rotation speed of the cooling fan 9a when the defrosting operation of the cooling evaporator is performed is selected to be the same as that in the normal operation mode.

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

Then, it is determined whether or not the vegetable room cooling end condition is satisfied (step S308). In the refrigerator of the present embodiment, when the vegetable room temperature T _V detected by the vegetable room temperature sensor 43 is equal to or lower than the vegetable room cooling end temperature T _{V_off} (=6 ℃) and is equal to or lower than (T _V≤T_{V_off}), step S307 is established. When step S308 is satisfied (Yes), the vegetable compartment damper 19 is closed, the frozen vegetable operation is ended, and the operation shifts to the freezing operation for cooling the freezing compartment 7 (step S309).

If step S308 is not satisfied (No), then it is determined whether or not the defrosting operation end condition of the refrigeration evaporator is satisfied (step S310). The defrosting operation end condition of the refrigeration evaporator is established when the temperature T _{R_evp} of the refrigeration evaporator is equal to or higher than the defrosting operation end temperature T _{RD_off} (=2 ℃) of the refrigeration evaporator (T _{R_evp}≥T_{RD_off}). If step S310 is true (Yes), the cooling fan 9a is stopped, and the defrosting operation of the cooling evaporator is completed (step S311).

If step S310 is not satisfied (No), it is then determined whether or not the frozen vegetable operation or the freezing operation termination condition is satisfied (step S312). In the refrigerator of the present embodiment, step S312 is established when the vegetable compartment shutter 19 is in the closed state and the freezing compartment temperature T _F is the freezing operation end temperature T _{F_off} (= -22.5 ℃) or less (T _F≥T_{F_off}), or when the frozen vegetable operation or the continuation time of the freezing operation reaches a predetermined value (42.5 minutes). If step S312 is not satisfied (No), the routine returns to the determination of step S308.

If step S312 is satisfied (Yes), the three-way valve 52 is set to state 3 (full-closed mode), and a refrigerant recovery operation is performed to recover the refrigerant in the refrigeration evaporator 14b to the heat radiation unit side (step S313). At this time, the cooling fan 9b continues to be driven.

Next, a determination is made as to whether or not to switch to the normal operation mode (step S314). In the refrigerator of the present embodiment, when it is satisfied that the refrigerating room temperature T _R detected by the refrigerating room temperature sensor 41 is equal to or lower than the refrigerating operation start temperature T _{R_on} (=5.5 ℃) and the freezing room temperature T _F detected by the freezing room temperature sensor 42 is equal to or lower than the frozen vegetable operation start temperature T _{F_on} (= -18 ℃) and is equal to or lower than the freezing vegetable operation start temperature T _R≤T_{F_on} (T _R≤T_{_on}), the process returns to the normal operation mode (step S101 in fig. 7) while the process of step S314 is true (Yes).

If step S314 is not satisfied (No), then the cooling operation is performed (step S315). The cooling operation is started by: the three-way valve 52 is set to state 1 (refrigeration mode), the compressor 24 is driven at a speed of 3 (2500 min ^-1), the refrigeration fan 9a is driven at a speed of 3 (2000 min ^-1), the freezing fan 9b is stopped, and the vegetable room barrier 19 is closed.

Next, it is determined whether or not the freezing chamber 7 is under a high load (step S316). In the refrigerator of the present embodiment, when the freezing chamber temperature T _F detected by the freezing chamber temperature sensor 42 is the high load determination temperature T _{F_high} (= -10 ℃) or higher (T _F≥T_{F_high}), step S316 is established (Yes). If step S316 is true (Yes), the refrigerant recovery operation is performed (step S304), and the operation is switched to the overload mode (step S305). After the start of the cooling operation, the determination in step S316 is skipped until a predetermined time (5 minutes) elapses.

If step S316 is not satisfied (No), the process proceeds to a determination as to whether or not the cooling operation end condition is satisfied (step S317). In the refrigerator of the present embodiment, step S317 is established when the refrigerating chamber temperature T _R is equal to or lower than the refrigerating operation end temperature T _{R_off} (=2.5 ℃) or when the duration of the refrigerating operation in the overload mode reaches a predetermined value (20.5 minutes) (T _R≤T_{R_off}). If step S317 is not satisfied (No), the routine returns to the determination of step S316 again, and if step S317 is satisfied (Yes), the three-way valve 52 is set to state 3 (full-closed mode), and a refrigerant recovery operation is performed to recover the refrigerant in the refrigeration evaporator 14a to the heat radiation unit side (step S318). At this time, the cooling fan 9a continues to be driven.

Next, a determination is made as to whether or not to switch to the normal operation mode (step S319). In the refrigerator of the present embodiment, when it is satisfied that the refrigerating room temperature T _R detected by the refrigerating room temperature sensor 41 is equal to or lower than the refrigerating operation start temperature T _{R_on} (=5.5 ℃) and the freezing room temperature T _F detected by the freezing room temperature sensor 42 is equal to or lower than the frozen vegetable operation start temperature T _{F_on} (= -18 ℃) and is equal to or lower than the freezing vegetable operation start temperature T _R≤T_{F_on} (T _R≤T_{R_on}), the step S318 is true (Yes), and the normal operation mode is returned (step S109 in fig. 7).

If the "high-load mode cooling operation" is selected in step S403, the control proceeds to step S315 to start the cooling operation, and if the "high-load mode frozen vegetable/freezing operation" is selected in step S503, the control proceeds to step S306 to start the frozen vegetable operation, and then 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 for 2 minutes when the compressor 24 is driven at a speed of 1 (800 min ^-1) and the cooling fan 9a is driven at a speed of 2 (1500 min ^-1), and for 1.5 minutes when the compressor 24 is driven at a speed of 3 (2500 min ^-1) and the cooling fan 9a is driven at a speed of 3 (2000 min ^-1). The refrigerant recovery operation in step S112 and step S302 was performed for 2.5 minutes when the compressor 24 was driven at a speed of 2 (1400 min ^-1) and the cooling fan 9b was driven at a speed of 1 (1200 min ^-1), and for 1.5 minutes when the compressor 24 was driven at a speed of 4 (1400 min ^-1) and the cooling fan 9b was driven at a speed of 2 (2000 min ^-1).

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

The circulation air volume of the freezing chamber 7 at the rotation speed (speed 1=1200min ^-1) of the freezing fan 9b in the normal operation mode was 0.55m ³/min in the state where the vegetable chamber damper 19 was opened (during the frozen vegetable operation), 0.6m ³/min in the state where the vegetable chamber damper 19 was closed (during the frozen operation), and 0.07m ³/min in the state where the vegetable chamber damper 19 was opened (during the frozen vegetable operation).

The circulation air volume of the refrigerating chamber 2 in the refrigerating operation in the high load mode or the overload mode at the rotation speed (speed 3=2000 min ^-1) of the refrigerating fan 9a is 0.52m ³/min. The circulation air volume of the freezing chamber 7 at the rotation speed (speed 2=2000 min ^-1) of the freezing fan 9b in the high load mode was 0.92m ³/min in the state where the vegetable chamber damper 19 was opened (during the frozen vegetable operation), 1.0m ³/min in the state where the vegetable chamber damper 19 was closed (during the frozen operation), and 0.12m ³/min in the state where the vegetable chamber damper 19 was opened (during the frozen vegetable operation).

Fig. 9 is a time chart showing a state in which the refrigerator of the present embodiment is set in an environment of 32 ℃ and a relative humidity of 70% and a steady cooling operation is performed in a normal operation mode. Further, the maintenance temperature level of the refrigerating chamber 2 is set to "medium", the maintenance temperature level of the freezing chamber 7 is set to "medium", and the fresh air cooling chamber 35 is set to "temperature level 1".

The elapsed time t ₀ is an elapsed time at which the cooling operation (step S101 in fig. 7) for cooling the refrigerating chamber 2 is started. In the cooling operation in the normal operation mode, the three-way valve 52 is controlled to be in the state 1 (cooling mode), and the compressor 24 is driven at the speed 1 (800 min ^-1) to supply the refrigerant to the cooling evaporator 14a, so that the temperature of the cooling evaporator 14a is lowered. In this state, the cooling fan 9a is driven at a speed of 2 (1500 min ^-1), so that air having a low temperature by passing through the cooling evaporator 14a is blown into the cooling chamber 2 from the cooling chamber outlet 11a (see fig. 2), and the cooling 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 ℃, which is higher than the time-average temperature of the refrigeration evaporator 14b during the refrigeration operation, which will be described later, by-24 ℃. In general, the higher the evaporator temperature (evaporation temperature), the higher the refrigeration cycle coefficient of performance (ratio of the amount of heat absorption 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 set to a low temperature, and the refrigerating chamber 2 needs to be maintained at the refrigerating temperature, so that the rotation speeds of the refrigerating fan 9a and the compressor 24 are controlled so as to increase the temperature of the refrigerating evaporator 14a, thereby improving the energy saving performance. At the elapsed time T ₁, the refrigerating room temperature T _R detected by the refrigerating room temperature sensor 41 is lowered to the refrigerating operation end temperature T _R＿off, and the refrigerating operation is switched to the refrigerant recovery operation (steps S104, S105 of fig. 7). In the refrigerant recovery operation, the three-way valve 52 is controlled to be in the state 3 (full-closed mode), the compressor 24 is driven at a speed of 1 (800 min ^-1), the cooling fan 9a is driven at a speed of 2 (1500 min ^-1), and the refrigerant in the cooling evaporator 14a is recovered for 2 minutes (Δt _A1 =2 min). This can suppress a decrease in cooling efficiency due to shortage of refrigerant in the following frozen vegetable operation and freezing operation. In this case, the cooling fan 9a is driven, so that the residual refrigerant in the cooling evaporator 14a can be used for cooling the refrigerating chamber 2, and the pressure drop in the cooling evaporator 14a can be alleviated by heating the air in the refrigerating chamber 2. This can suppress an increase in the specific volume of the refrigerant sucked into the compressor 24, and can recover a large amount of refrigerant in a short time, thereby improving the cooling efficiency.

When the refrigerant recovery operation is completed (the elapsed time t ₂), it is determined whether or not the defrosting operation of the refrigerating evaporator is to be performed, and since the setting of the cooling chamber 35 is "temperature level 1", the refrigerating fan 9a is driven at speed 1 (900 min ^-1) to perform the defrosting operation of the refrigerating evaporator (steps S106 and S107 in fig. 7). This reduces the temperature rise of the refrigerating chamber 2 by the cooling effect of the frost and the cold storage heat of the refrigerating evaporator 14a while the temperature of the refrigerating evaporator 14a increases. Further, at the elapsed time T ₂, since the freezing chamber temperature T _F detected by the freezing chamber temperature sensor 42 is equal to or higher than the frozen vegetable operation start temperature T _{F_on}, the frozen vegetable operation is started, the vegetable chamber 6 is cooled, and the vegetable chamber temperature T _V is lowered. In the frozen vegetable operation, the three-way valve 52 is controlled to be in state 2 (freezing mode), the compressor 24 is driven at speed 2 (1400 min ^-1), the refrigerant is supplied to the freezing evaporator 14b, and the freezing evaporator 14b is set to a low temperature. In this state, the vegetable room damper 19 is opened, and the freezing fan 9b is driven at a speed of 1 (1200 min ^-1), whereby the freezing room 7 and the vegetable room 6 are cooled by the air cooled by the freezing evaporator 14 b.

At the elapsed time T ₃, the vegetable room temperature T _V detected by the vegetable room temperature sensor 43 reaches the vegetable room cooling end temperature T _V＿off, and the vegetable room shutter 19 is closed, whereby the operation is switched to the cooling operation (steps S111 and S112 in fig. 7).

Then, at the elapsed time T ₄, the temperature T _Revp of the refrigeration evaporator 14a detected by the refrigeration evaporator temperature sensor 40a reaches the refrigeration evaporator defrosting operation end temperature T _{RD_off}, and therefore the refrigeration fan 9a is stopped and the refrigeration evaporator defrosting operation ends (steps S113 and S114 in fig. 7).

At the elapsed time T ₅, the freezing chamber temperature T _F detected by the freezing chamber temperature sensor 42 reaches the freezing operation end temperature T _F＿off, and the vegetable chamber shutter 19 is closed, and thus the freezing operation ends (step S115 of fig. 7). At this time, since the refrigerating room temperature T _R detected by the refrigerating room temperature sensor 41 reaches the refrigerating operation start temperature T _R＿on or higher, the refrigerating operation start condition is satisfied (step S116 in fig. 7), and the refrigerant recovery operation is performed (step S117 in fig. 7). In the refrigerant recovery operation, the three-way valve 52 is controlled to be in the state 3 (full-closed mode), the compressor 24 is driven at the speed 2 (1400 min ^-1), the freezing fan 9b is driven at the speed 1 (1200 min ^-1), and the refrigerant in the freezing evaporator 14b is recovered for 1.5 minutes (Δt _B1 =1.5 min). This can suppress a decrease in cooling efficiency due to shortage of refrigerant in the subsequent cooling operation. In this case, the cooling fan 9b is driven, so that the residual refrigerant in the freezing evaporator 14b can be used for cooling the freezing chamber 7 effectively and flexibly, and the pressure drop in the freezing evaporator 14b can be alleviated by heating the air in the freezing chamber 7. This can suppress an increase in the specific volume of the refrigerant sucked into the compressor 24, and can recover a large amount of refrigerant in a short time, thereby improving the cooling efficiency.

The operation of cooling the freezing chamber 7 is a vegetable freezing operation (t 2 to t 3), a freezing operation (t 3 to t 5), and a refrigerant recovery operation (t 5 to t 6), and the freezing fan 9b and the compressor 24 are controlled so that the time-average temperature of the freezing evaporator 14b during these operations is about-24 ℃. The time average value of the refrigerating chamber discharge air temperature during the freezing operation, the refrigerant recovery operation, and the defrosting operation of the refrigerating evaporator in which the refrigerating fan 9a is driven is-1.5 ℃, which is a temperature higher than the arithmetic average value (-8 ℃) of the freezing chamber maintenance temperature T _{F_keep} (-20 ℃) and the refrigerating chamber maintenance temperature T _{R_keep} (4 ℃).

The refrigerating operation is restarted after the lapse of time t ₆ from the end of the refrigerant recovery operation (step S101 in fig. 7), and thereafter, the above operation is periodically repeated, the refrigerating chamber 2 is maintained at about 4 ℃, the freezing chamber 7 is maintained at about-20 ℃, and the vegetable chamber is maintained at about 7 ℃.

Fig. 10 is a time chart showing an operation state when the refrigerator of the present embodiment is set in an environment of 32 ℃ and a load cooling test by JISC9801-3:2015 is performed. In a refrigerator, it is very important to perform cooling operation stably without opening and closing a door, and to perform cooling well when a practical load such as food is placed. In addition to fully considering the general method of using a refrigerator, JISC9801-3:2015 defines a "load cooling test" in which a practical load (hereinafter, referred to as a practical load) is assumed to be applied, and defines that water isothermal to the outside air temperature is used as a practical load, 12g of standard water is applied to a refrigerating compartment at a rated capacity of a refrigerating temperature zone compartment (refrigerating compartment and vegetable compartment) of 1L, and 4g of standard water is applied to a freezing compartment at a rated capacity of a freezing zone compartment (freezing compartment) of 1L.

In the state where the cooling operation (see fig. 9) is performed in the steady cooling operation, the door 2a of the refrigerating compartment 2 is opened for 1 minute in accordance with the procedure defined in jis c9801-3:2015, and as a practical load of the refrigerating temperature zone compartments (refrigerating compartment 2 and vegetable compartment 6), 5064g (load of the refrigerating temperature zone compartments (refrigerating compartment 2 and vegetable compartment 6) in the rated capacity 422L) of water at 32 ℃ is sealed in a 500mL plastic bottle and set at a predetermined position in the refrigerating compartment 2. Next, the door 5a of the freezing chamber 7 (lower-stage freezing chamber 5) was opened for 1 minute, and 720g (a load of the freezing temperature zone chamber (freezing chamber 7) of 180L in rated capacity) of water at 32 ℃ was set at a predetermined position in the freezing chamber 7 (lower-stage freezing chamber 5).

Thus, first, the refrigerating compartment temperature T _R rises and exceeds the refrigerating compartment high load determination temperature T _{R_high}, and therefore, it is determined that the refrigerating compartment 2 is under a high load (step S110 in fig. 7). At this time, the refrigerating chamber temperature T _R exceeds the refrigerating chamber high load determination temperature T _{R_high}, and is determined as a high load, but the freezing chamber temperature T _F does not reach the high load determination temperature T _{F_high}. Therefore, step S301 of fig. 8 is true (Yes), and step S302 is not true (No), so that it is next determined whether or not to perform the refrigerant recovery operation (step S401 of fig. 8). Since the operation mode at the time of the determination in step S110 is the cooling operation, it is determined that the refrigerant recovery operation is necessary (Yes in step 401 in fig. 8), and the refrigerant recovery operation (step S402 in fig. 8) is performed in which the refrigerant in the freezing evaporator 14b is recovered for 2.5 minutes (Δt _A2 =2.5 minutes) while the compressor 24 is driven at the speed 2 (1400 min ^-1) and the freezing fan 9b is driven at the speed 1 (1200 min ^-1). At this time, the freezing fan 9b is driven, and the freezing chamber 7 is cooled by the heat absorption action of the residual refrigerant in the freezing evaporator 14b (freezing chamber cooling operation (F)).

After the lapse of time t ₀', the three-way valve 52 is controlled to be in state 1 (refrigeration mode), and the high-load mode refrigeration operation is performed in which the compressor 24 is driven at speed 3 (2500 min ^-1), the refrigeration fan 9a is driven at speed 3 (2000 min ^-1), and the refrigeration fan 9b is stopped (steps S403 and S315 in fig. 8).

The practical load applied to the freezing chamber 7 (lower-stage freezing chamber 5) increases the freezing chamber temperature T _F and exceeds the high-load determination temperature T _{F_high}, but since the step S316 shown in fig. 8 is not established until 5 minutes has elapsed after the transition to the cooling operation, the high-load mode cooling operation is continued.

Since the minimum elapsed time after the establishment of the cooling operation switching condition, i.e., 5 minutes, is elapsed at the elapsed time t ₁, step S316 shown in fig. 8 is established (Yes), and the refrigerant recovery operation (step S304 in fig. 8) is performed, and the operation is switched to the overload mode (step S305 in fig. 8) at the elapsed time t1. In the refrigerant recovery operation at this time, the three-way valve 52 is controlled to be in the state 3 (full-closed mode), the compressor 24 is driven at the speed 3 (2500 min ^-1), the cooling fan 9a is driven at the speed 3 (2000 min ^-1), and the refrigerant in the cooling evaporator 14a is recovered for 1.5 minutes (Δt _B2 =1.5 min). The refrigerant recovery operation is completed at the elapsed time t ₁'. In the refrigerant recovery operation, the cooling fan 9a is driven, and the refrigerating chamber 2 is cooled by the heat absorption action of the residual refrigerant in the refrigerating evaporator 14 a.

The elapsed time t ₁ 'from the elapsed time t ₀' is an operation state of cooling the refrigerating chamber (refrigerating chamber cooling operation (R)).

The operation of cooling the frozen vegetables in the freezing chamber 7 is started after the lapse of time t ₁ in the overload mode (step S306 in fig. 8). The frozen vegetable operation in the overload mode is performed in the following state: the three-way valve is controlled to state 2 (freezing mode), the compressor 24 is driven at speed 4 (3600 min ^-1), the freezing fan 9b is driven at speed 2 (2000 min ^-1), and the vegetable room barrier 19 is opened. By this operation, the freezing chamber 7 and the vegetable chamber 6 are cooled. At this time, the cooling fan 9a is driven at a speed of 1 (900 min ^-1) to perform the defrosting operation of the cooling evaporator (step S307 in fig. 8). At the elapsed time T ₂, the temperature T _Revp of the refrigeration evaporator 14a detected by the refrigeration evaporator temperature sensor 40a reaches the refrigeration evaporator defrosting operation end temperature T _{RD_off}, and therefore the refrigeration fan 9a is stopped, and the refrigeration evaporator defrosting operation ends (steps S310 and S311 in fig. 8).

At the elapsed time T ₃, the vegetable room temperature T _V detected by the vegetable room temperature sensor 43 is equal to or lower than the vegetable room cooling end temperature T _{V_off} (T _V≤T_{V_off}), and the vegetable room shutter 19 is closed, and the operation is switched to the cooling operation (steps S308 and S309 in fig. 8).

At the elapsed time t ₄, since the elapsed time from the start of the frozen vegetable operation in the overload mode reaches the predetermined value (42.5 min), the frozen vegetable/frozen operation end condition is satisfied (step S312 in fig. 8), the frozen operation ends, and the operation shifts to the refrigerant recovery operation. In the refrigerant recovery operation at this time, the three-way valve 52 is controlled to be in the state 3 (full-closed mode), the compressor 24 is driven at the speed 4 (3600 min ^-1), the freezing fan 9b is driven at the speed 2 (2000 min ^-1), and the refrigerant in the freezing evaporator 14b is recovered for 1.5 minutes (Δt _C2 =1.5 min). The refrigerant recovery operation is completed at the elapsed time t ₄'. In the refrigerant recovery operation, the freezing fan 9b is driven, whereby the freezing chamber 7 is cooled by the heat absorption action of the residual refrigerant in the freezing evaporator 14 b. As described above, the elapsed time t ₁'～t₄' is an operation for cooling the freezing chamber 7 (freezing chamber cooling operation (F)).

Next, it is determined whether or not to switch to the normal operation mode (step S314 in fig. 8), but since the refrigerating chamber temperature T _R and the freezing chamber temperature T _F are higher than the refrigerating operation start temperature T _{R_on} and the frozen vegetable operation start temperature T _{F_on} at the elapsed time T ₄', the switching to the overload mode refrigerating operation is not established (step S315 in fig. 8). Thus, the refrigerating operation in the overload mode is performed, that is, the three-way valve 52 is controlled to be in the state 1 (refrigerating mode), the compressor 24 is driven at the speed 3 (2500 min ^-1), the refrigerating fan 9a is driven at the speed 3 (2000 min ^-1), and the freezing fan 9b is stopped (step S315 in fig. 8).

When the elapsed time t ₅ has reached the predetermined value (20.5 min), the refrigerating operation end condition is satisfied (step S317 in fig. 8), and the operation shifts to the refrigerant recovery operation (step S318 in fig. 8). In the refrigerant recovery operation at this time, the three-way valve 52 is controlled to be in the state 3 (full-closed mode), the compressor 24 is driven at the speed 3 (2500 min ^-1), the cooling fan 9a is driven at the speed 3 (2000 min ^-1), and the refrigerant in the cooling evaporator 14a is recovered for 1.5 minutes. This refrigerant recovery operation is completed at the elapsed time t ₅ '(similar control to the refrigerant recovery operation performed at the elapsed time t ₁～t₁'). As described above, the elapsed time t ₄'～t₅' is the operation of cooling the refrigerating chamber 2 (refrigerating chamber cooling operation (R)).

Thereafter, the refrigerating compartment 2, the freezing compartment 7, and the vegetable compartment 6 are cooled by the same control as the elapsed time t ₁'～t₅'. Specifically, the elapsed time t ₅～t₈、t₉～t₁₂、t₁₃～t₁₇ is a freezing chamber cooling operation, and the elapsed time t ₈～t₉、t₁₂～t₁₃、t₁₇～t₁₉ is a refrigerating chamber cooling operation. In addition, at t ₅～t₆、t₉～t₁₀、t₁₃～t₁₄, a defrosting operation of the refrigerating evaporator is performed.

Whether or not the utility load is sufficiently cooled can be judged by whether or not the refrigerating chamber temperature T _R is cooled to below the refrigerating chamber maintenance temperature T _Rkeep +1deg.C, and whether or not the freezing chamber temperature T _F is cooled to below the freezing chamber maintenance temperature T _Fkeep +1deg.C. The refrigerating compartment maintaining temperature T _Rkeep +1 c or less and the freezing compartment maintaining temperature T _Fkeep +1 c or less may not be satisfied at the same time. In the present specification, a state from the time when a load is placed in the refrigerating chamber 2 to the time when the load is considered to be sufficiently cooled by the practical loads placed in the refrigerating chamber 2 and the freezing chamber 7 is referred to as a load cooling section. In the refrigerator of the present embodiment, at T ₁₆ shown in fig. 10, the freezing chamber temperature T _F reaches the freezing chamber maintenance temperature T _{F_keep} +1 ℃, and at T ₁₈, the refrigerating chamber temperature T _R reaches the refrigerating chamber maintenance temperature T _{R_keep} +1 ℃, and therefore, from T ₀ where the utility load is put into the refrigerating chamber 2 to T ₁₈ where the utility load regarded as the refrigerating chamber 2 and the freezing chamber 7 is sufficiently cooled is a load cooling section.

Here, in the refrigerator of the present embodiment, the cooling state of the utility load placed in the refrigerator compartment 2 and the freezer compartment 7 can be determined by the refrigerator compartment temperature T _R detected by the refrigerator compartment temperature sensor 41 and the freezer compartment temperature TF detected by the freezer compartment temperature sensor 42, but in order to more reliably determine the cooling state of the utility load, the temperatures representing the refrigerator compartment 2 and the freezer compartment 7 may be measured by a method prescribed by JISC9801-1:2015, and the cooling state of the utility load may be determined based on the temperatures.

When the time T ₁₉ has elapsed, it is determined whether or not to switch to the normal operation mode (step S319 in fig. 8), and the refrigerating chamber temperature T _R is equal to or lower than the refrigerating operation start temperature T _{R_on} (T _R≤T_{R_on}), and the freezing chamber temperature T _F is equal to or lower than the frozen vegetable operation start temperature T _{F_on} (T _R≤T_{F_on}), the overload mode is ended (Yes in step S319 in fig. 8), and after T ₁₉, cooling in the normal operation mode is performed.

In this way, since the utility load is put into the refrigerator compartment 2 and the freezer compartment 7 at t ₀, the refrigerator compartment 2 and the freezer compartment 7 are both in a high-load state, and thus, the overload mode is set, and the operation of cooling the refrigerator compartment 2 (refrigerator cooling operation) and the operation of cooling the freezer compartment 7 (freezer cooling operation) are alternately performed, and at t ₁₈, the utility load is sufficiently cooled, and the normal mode is returned.

Before T ₁₈ is sufficiently cooled, the freezing chamber temperature T _F assumes a maximum value T _F1 (= -7 ℃) at T ₁, a maximum value T _F2 (= -11 ℃) at T ₅', a maximum value T _F3 (= -14 ℃) at T ₉, a maximum value T _F4 (= -16.5 ℃) at T ₁₃, and the respective maximum values gradually decrease (T _F1＞T_F2＞T_F3＞T_F4).

In the operation in the load cooling section (T ₀～t₁₈), the time-average temperature T _{Revp_ave} of the refrigeration evaporator 14a in the refrigerator cooling operation (t₀'～t₁',t₄'～t₅',t₈～t₉,t₁₂～t₁₃,t₁₇～t₁₈) for cooling the refrigerator 2 is-6.0 ℃, and the time-average temperature T _{Fevp_ave} of the freezing evaporator 14b in the freezer cooling operation (t₀～t₀',t₁'～t₄',t₅'～t₈,t₉～t₁₂,t₁₃～t₁₇) for cooling the freezer 7 is-23.0 ℃, which is T _{Revp_ave}＞T_{Fevp_ave}.

In addition, in the case of the optical fiber, A ratio of time R _R =34% from a time point when the load is placed to a time point when the normal operation mode (t ₀～t₁₇) is restarted to be a cooling operation of the refrigerating chamber (a time ratio of t₀'～t₁',t₄'～t₅',t₈～t₉,t₁₂～t₁₃,t₁₆～t₁₇ in the operation of t ₀～t₁₇), The ratio of the time rate (the time rate of t₀～t₀',t₁'～t₄',t₅'～t₈,t₉～t₁₂,t₁₃～t₁₆ in the operation of t ₀～t₁₇) of the freezing chamber vegetable chamber cooling operation to the freezing chamber 7, R _F =66%, and the ratio of both R _F/R_R =1.94. on the other hand, the outside air temperature was set to T _out (=32 ℃), the air-side heat transfer area of the refrigeration evaporator 14a was set to a _Revp(＝0.993m²), the time-average temperature during the refrigeration compartment cooling operation of the refrigeration evaporator 14a was set to T _{Revp_ave} (= -6.0 ℃), The refrigerating compartment maintaining temperature was set to T _{R_keep} (=4.0 ℃) and the air-side heat transfer area of the freezing evaporator 14b was set to a _Fevp(＝1.146m²), the time-average temperature during the freezing compartment cooling operation of the freezing evaporator 14b was set to T _{Fevp_ave} (= -23.0 ℃), The freezing chamber maintaining temperature was set to T _{F_keep} (= -20 ℃), the rated capacity of the refrigerating temperature zone chamber (refrigerating chamber and vegetable chamber) was set to V _R (=422L), the rated capacity of the freezing chamber was set to V _F (=180L), The specific heat of water was C _W (= 4.186 kJ/kg) and the specific heat of ice was C _i (=2.05 kJ/kg) and the latent heat of solidification of water was L _W (=333.6 kJ/kg), If calculation {A_Revp×(T_{R_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, R _F/R_R (=1.94) is higher than it is. by controlling the above, both the large-capacity freezing chamber and the practical cooling performance can be achieved (details will be described later).

The configuration and control method of the refrigerator of the present embodiment are described above, and effects of the refrigerator of the present embodiment will be described below.

The refrigerator of the present embodiment includes a refrigerating chamber 2 (first refrigerating temperature zone chamber), a vegetable chamber 6 (second refrigerating temperature zone chamber), and a freezing chamber 7, wherein a refrigerating evaporator 14a (first evaporator) and a refrigerating fan 9a (first fan) are provided on the back of the refrigerating chamber 2, a freezing evaporator 14b (second evaporator) and a freezing fan 9b (second fan) are provided on the back of the freezing chamber 7, and the refrigerator includes a refrigerating air passage 111 (first air passage) through which cooling air having exchanged heat with the refrigerating evaporator 14a flows to the refrigerating chamber 2 by driving the first fan and a refrigerating vegetable air passage 112 (second air passage) through which cooling air having exchanged heat with the freezing evaporator 14b flows to the freezing chamber 7 and the vegetable chamber 6 by driving the freezing fan 9b, and an air flow blocking means (heat-insulating partition wall 28) for blocking air flow between the first air passage and the second air passage. Accordingly, even when the load of the vegetable room increases due to, for example, the vegetable room accommodating therein food having a relatively high temperature or the gap being formed between the vegetable room door and the heat insulation box due to sandwiching of food or the like, the vegetable room and the refrigerating room can be cooled independently, it is not necessary to cool the refrigerating room together with the vegetable room, and excessive cooling of the refrigerating room can be suppressed, and therefore, a decrease in cooling efficiency of the refrigerating room can be prevented. Further, unlike the structure in which the vegetable compartment is indirectly cooled by the cold air of the freezing compartment via the partition wall or the like as in patent document 1, the air having undergone heat exchange with the freezing evaporator can be sent to the vegetable compartment for cooling, and therefore, the cooling efficiency of the freezing compartment can be prevented from being lowered due to excessively maintaining the freezing compartment at a low temperature. That is, a refrigerator is configured such that a problem of a reduction in cooling efficiency of the entire refrigerator, that is, a refrigerator having a high cooling efficiency of the entire refrigerator, is less likely to occur in order to cool a load of a part of the storage compartments.

The refrigerator of the present embodiment includes: a cooling air passage 111 (first air passage) for passing cooling air having exchanged heat with the cooling evaporator 14a through the cooling chamber 2 (first cooling temperature zone chamber), the freezing chamber 7, and the vegetable chamber 6 (second cooling temperature zone chamber) having the largest rated capacity among the cooling chamber 2 (first cooling temperature zone chamber); and a frozen vegetable air passage 112 (second air passage) for allowing the cooling air having exchanged heat with the freezing evaporator 14b to flow to the freezing compartment 7 and the vegetable compartment 6, and further includes an air flow blocking means (heat insulating partition wall 28) for blocking the flow of air between the refrigerating air passage 111 and the frozen vegetable air passage 112. Generally, the larger the rated capacity, the more food the user can store, and therefore, in many cases, the cooling load of the storage room having a larger rated capacity is larger. Therefore, by providing the air flow shut-off means (the heat insulation partition wall 28) so that the air does not flow between the cooling air passage 111 and the frozen vegetable air passage 112 for circulating the cooling air to the refrigerating chamber 2 having the largest rated capacity among the refrigerating chamber 2 (the first refrigerating temperature zone chamber), the freezing chamber 7, and the vegetable chamber 6 (the second refrigerating temperature zone chamber), it is possible to prevent the temperature of the food or the like in the other freezing chamber or the vegetable chamber from rising due to the load of the storage chamber having the largest rated capacity, and a refrigerator having a high cooling efficiency can be constituted.

The refrigerator of the present embodiment includes a cooling air passage 111 (first air passage) for passing cooling air to a refrigerating chamber 2 (first refrigerating temperature zone chamber) which is the uppermost storage chamber, and a frozen vegetable air passage 112 (second air passage) for passing cooling air to a freezing chamber 7 and a vegetable chamber 6 which are positioned below the refrigerating chamber 2, and further includes an air passage blocking means (heat insulating partition wall 28) for blocking the air passage between the cooling air passage 111 and the frozen vegetable air passage 112. In general, in an environment (for example, a kitchen) in which a refrigerator is installed, when active air stirring is not performed by an air conditioner or the like, a temperature distribution (temperature stratification) in the vertical direction is formed, and the air temperature tends to be higher as it goes upward. Therefore, the uppermost storage chamber is liable to flow in air having a high temperature during the opening and closing operation of the door, and the load is liable to increase. Therefore, the refrigerator according to the present embodiment is provided with the air flow blocking means (the heat insulating partition wall 28) so that the air does not flow between the cooling air passage 111 through which the cooling air flows to the refrigerating chamber 2 (the first refrigerating temperature zone chamber) which is the uppermost storage chamber and the frozen vegetable air passage 112 through which the cooling air flows to the freezing chamber 7 which is the lower storage chamber and the vegetable chamber 6, and thus, it is possible to construct a refrigerator having a high cooling efficiency in which the temperature of foods and the like in the other storage chambers (the freezing chamber and the vegetable chamber) is less likely to rise due to the influence of the load of the uppermost storage chamber.

Further, as shown in the refrigerator of the present embodiment, in the refrigerator in which the refrigerating chambers (freezing temperature zone chambers), the freezing chambers (freezing temperature zone chambers) and the vegetable chambers (refrigerating temperature zone chambers) are arranged in this order from above, the freezing chamber adjacent to the uppermost refrigerating chamber (freezing temperature zone chamber) is a storage chamber maintained at a low temperature, and therefore, there is a tendency that the temperature of the food or the like in the freezing chamber increases due to the influence of the load placed in the refrigerating chamber. That is, the refrigerator provided with the air flow blocking means (heat insulating partition wall 28) for blocking the flow of air between the cooling air duct 111 and the frozen vegetable air duct 112 is particularly effective in a refrigerator in which a cooling chamber (cooling temperature zone chamber), a freezing chamber (cooling temperature zone chamber), and a vegetable chamber (cooling temperature zone chamber) are arranged in this order from above.

The refrigerator of the present embodiment includes a refrigerating air passage 111 (first air passage) for circulating cooling air to a refrigerating chamber 2 (first refrigerating temperature zone chamber) which is a storage chamber having the largest total circumference of a sealing member (gasket), and a frozen vegetable air passage 112 (second air passage) for circulating cooling air to a freezing chamber 7 and a vegetable chamber 6, and further includes an air-circulation shut-off means (heat-insulating partition wall 28) for shutting off the circulation of air between the refrigerating air passage 111 and the frozen vegetable air passage 112. The door sealing portion may generate a minute gap by sandwiching food, food packaging materials, or the like, and thus, inflow and outflow of outside air and air in the storage chamber may occur, resulting in an increase in load. Since this is more likely to occur as the sealing length between the door leaf and the heat-insulating box becomes longer, that is, as the total circumference of the sealing member becomes longer, the refrigerator of the present embodiment includes the cooling air passage 111 for shutting off the cooling air to the refrigerating compartment 2 which is the storage compartment having the largest total circumference of the sealing member (gasket) and the air flow shut-off means (heat-insulating partition wall 28) for shutting off the air flow between the freezing compartment 7 located in the lower layer of the refrigerating compartment 2 and the frozen vegetable air passage 112 of the vegetable compartment 6, and therefore, it is possible to prevent the temperature of the foods and the like in the other storage compartments (freezing compartment and vegetable compartment) from rising due to the influence of the load of the storage compartment having the largest total circumference of the sealing member (gasket), and the refrigerator having high cooling efficiency can be constituted.

In the refrigerator of the present embodiment, in the steady cooling operation, if the maintenance temperature of the refrigerating chamber 2 is set to T _{R_keep} (about 4 ℃ in the case of setting to "medium"), the maintenance temperature of the freezing chamber 7 is set to T _{F_keep} (about-20 ℃ in the case of setting to "medium"), and the time-average temperature of the refrigerating evaporator 14a in the refrigerating operation is set to T _{Revp_ave}, the rotation speed of the evaporator temperature adjusting means (the compressor 24 and the refrigerating fan 9 a) is controlled so as to satisfy the following (formula 1).

T _{Revp_ave}≥0.5×(T_{R_keep}+T_{F_keep}) (1)

In general, in a refrigeration cycle, when the rotation speeds of a compressor and a blower that blows air to an evaporator are controlled so that the time-average temperature of the evaporator increases during a cooling operation, the coefficient of performance of the refrigeration cycle increases, and the cooling efficiency increases. Therefore, in terms of improvement of cooling efficiency, it is effective to increase the time-average temperature of the evaporator when cooling the refrigerating compartment maintained at a high temperature. However, when there is a path through which cooling air for cooling the refrigerator compartment flows to the freezer compartment, the temperature of the freezer compartment maintained at a low temperature increases, and therefore the time-average temperature of the evaporator during the cooling operation cannot be sufficiently increased. Therefore, the refrigerator of the present embodiment is provided with an air flow blocking means (heat insulating partition wall 28) for blocking the flow of air between the cooling air duct 111 and the frozen vegetable air duct 112, and the rotation speed of the compressor 24 and the cooling fan 9a is controlled to sufficiently increase the time-average temperature of the cooling evaporator during the cooling operation, so that the relationship shown in (formula 1) is satisfied, thereby configuring a refrigerator with high cooling efficiency. In the case where there are a plurality of freezing chambers and the maintenance temperature thereof is set to be a plurality of temperatures, the temperature of the storage chamber that is the lowest temperature may be set to T _{F_keep} of (formula 1).

In the refrigerator of the present embodiment, in the steady cooling operation, when the difference between the refrigerating chamber maintaining temperature T _{R_keep} and the time average temperature T _{Revp_ave} of the refrigerating evaporator 14a in the refrigerating operation is set to Δt (=t _{R_keep}-T_{Revp_ave}), and the coefficient of performance of the refrigeration cycle with respect to the evaporator temperature is set to COP _th, the evaporator temperature adjustment means (the compressor 24 and the refrigerating fan 9 a) is controlled so as to satisfy expression (2). This makes it possible to efficiently perform the cooling operation in a range where the effectiveness of the increase in the air volume is high.

The reason will be described with reference to fig. 11 and 12. Fig. 11 (a) is a graph showing the relationship between the theoretical coefficient of performance COP _th (coefficient of performance at 100% of compressor efficiency) and the temperature of the refrigeration evaporator, and the reciprocal Δt ^-1(＝1/(T_{R_keep}-T_evp of the difference between the refrigeration compartment maintenance temperature T _{R_keep} and the temperature T _evp of the evaporator). Fig. 11 b is a graph showing a function (=d (COP _th)/dT_evp-d(ΔT^-1)/dT_evp) of differentiating the difference between Δt ^-1 and COP _th by the evaporator temperature T _evp.

Here, a method for solving the theoretical coefficient of performance COP _th shown in fig. 11 (a) will be described with reference to fig. 12. Fig. 12 is a mollier chart showing an operation state of a refrigeration cycle of a normal refrigerator. The state of the compressor (state 1) in which the refrigerant is sucked is determined by fixing the pressure on the low pressure side (evaporator side) to a pressure determined by the evaporator temperature (evaporation temperature) regardless of the pressure loss in the piping. In addition, the outside air temperature on the high-pressure side (condenser side) is set to a condensing temperature (two-phase temperature), and is fixed to a pressure determined by the condensing temperature. The refrigerant state at the condenser outlet (capillary inlet) is saturated liquid (state 3), the refrigerant state at the evaporator outlet is saturated vapor (state 5), the capillary tube and the piping from the evaporator to the compressor are set to perform heat exchange completely (action of the contact portion 57a in fig. 4), and the temperature at which the compressor sucks in the refrigerant is set to the condenser outlet temperature (state 1). The compressor discharge state (state 2) was determined by setting the compressor efficiency to 100% (adiabatic compression), and the evaporator inlet refrigerant state (state 4) was determined on the assumption that the capillary tube and the pipe from the evaporator to the compressor completely exchange heat (Δh1=Δh2 in fig. 4). By determining the outside air temperature and the evaporator temperature, the theoretical coefficient of performance COP _th can be calculated as the ratio (COP _th＝Q_th/W_th) of the theoretical cooling capacity Q _th to the theoretical compression power W _th based on the physical properties of the refrigerant. The theoretical coefficient of performance COP _th is an index indicating the cooling efficiency independent of the efficiency of the compressor. The relationship between the theoretical coefficient of performance COP _th and the evaporator temperature T _evp shown in fig. 11 (a) is calculated by setting the refrigerant to isobutane and the outside air temperature to T _out =32℃.

In addition, in order to perform good cooling, a predetermined amount of heat exchange needs to be obtained in the evaporator. If the change in temperature efficiency (the value of the difference between the evaporator inlet air temperature and the evaporator outlet air temperature divided by the difference between the evaporator inflow air temperature and the evaporator temperature) is ignored, a relationship is derived in which the air volume and the air temperature for obtaining the predetermined heat exchange amount are proportional to the inverse of the difference between the evaporator temperatures. By using the refrigerating compartment maintenance temperature T _{R_keep} as the air temperature, Δt ^-1 shown in fig. 11 (a) is calculated as an index indicating the magnitude of the air volume for obtaining the predetermined heat exchange amount. Further, Δt ^-1 shown in fig. 11 (a) is calculated by setting the refrigerating compartment maintenance temperature T _{R_keep} to 4 ℃.

COP _th and Δt ^-1 shown in fig. 11 (a) each monotonically increase with respect to the increase in the evaporator temperature T _evp, but the slopes of the two are different. Fig. 11 (b) shows a function of differentiating the difference between COP _th and Δt ^-1 by the evaporator temperature T _evp, and shows the difference in the slopes of both. That is, in the graph of FIG. 11 (b), in the range where the slope is positive (the range where the evaporator temperature T _evp is lower than about-1 ℃), the rate of increase of COP _th with respect to the increase of evaporator temperature T _evp is higher than the rate of increase of Δt ^-1 with respect to the increase of evaporator temperature T _evp, In order to improve COP _th, it can be said that it is advantageous to raise the evaporator temperature T _evp. On the other hand, in the range where the slope is negative (the range where the evaporator temperature T _evp is higher than about-1 ℃), the increase rate of COP _th with respect to the increase of the evaporator temperature T _evp is lower than the increase rate of Δt ^-1 with respect to the increase of the evaporator temperature T _evp, It can be said that the effectiveness of the increase in the air volume required to increase the evaporator temperature T _evp is reduced. That is, in order to set the graph of fig. 11 (b) to a positive slope range, the refrigerator is controlled so that d ²(COP_th)/dT_evp ²-d²(ΔT^-1)/dT_evp ² is equal to or greater than 0, and is operated in a range where the effectiveness of the air volume improvement is high. Therefore, in the refrigerator of the present embodiment, the evaporator temperature T _evp in fig. 11 is set to the time-average temperature T _{Revp_ave} of the refrigeration evaporator 14a during the cooling operation, and is controlled so as to satisfy (expression 2), whereby the cooling operation can be efficiently performed in a range where the efficiency of the air volume increase is high.

The refrigerator of the present embodiment has an operation mode in which the drive time of the cooling fan 9a of the cooling chamber 2 having the largest rated capacity is longer than the drive time of the freezing fan 9b in the steady cooling operation. Thus, the refrigerator compartment 2 having the largest rated capacity can be set as a storage compartment having a relatively high storage capacity with less temperature unevenness. In general, a state in which an active air flow is generated by driving the air blowing unit is called forced convection, and a weak air flow generated by a temperature difference (density difference) of air without blowing the air by the air blowing unit is called natural convection. When forced convection occurs in the space due to the blower unit, air actively moves to average the temperature in the space, and when the blower unit is stopped, natural convection occurs, and movement of air in the space is difficult to occur, so that temperature unevenness is easily generated, and particularly in a space having a large capacity, the temperature is more remarkable. If the temperature unevenness is large, there is a problem that the preservability of the food tends to be lowered depending on the place where the food is stored. Therefore, in the refrigerator of the present embodiment, by providing the operation mode in which the drive time of the cooling fan 9a of the cooling chamber 2 having the largest rated capacity is controlled to be longer than the drive time of the freezing fan 9b, the cooling chamber 2 can be set as a storage chamber having a relatively high storage property with less temperature unevenness.

The refrigerator of the present embodiment includes an operation mode in which the driving time of the cooling fan 9a of the cooling chamber 2, which is the storage chamber having the largest height, is longer than the driving time of the freezing fan 9 b. In general, since the temperature distribution becomes larger as the height dimension becomes larger, in the refrigerator of the present embodiment, the refrigerator can set the refrigerating chamber 2 to a storage chamber having a smaller temperature unevenness and a higher preservability by an operation mode in which the driving time of the refrigerating fan 9a of the refrigerating chamber 2 having the largest height dimension is longer than the driving time of the freezing fan 9 b.

The refrigerator of the present embodiment opens (cold air directing means) a refrigerator compartment outlet 11a of a refrigerator compartment air blowing path 11 provided on the back surface of the refrigerator compartment upward, and blows out air directed upward. In general, if food stored in the storage chamber blocks the flow of cooling air, there are cases where the temperature inside the storage chamber becomes uneven, or the resistance of the air passage increases and the air volume decreases, and the cooling efficiency decreases. Therefore, by opening the main refrigerator discharge port 11a of the refrigerator compartment blower 11 upward (cold air directing means), the upward directed air is blown out, and the cooling air flows forward along the ceiling surface of the refrigerator compartment 2 as indicated by the arrow in fig. 2, and therefore, even if a large amount of food is contained in the refrigerator compartment 2, the flow of the cooling air is hardly hindered by the food, and it is difficult to cause temperature unevenness in the storage compartment, or the air flow rate decreases due to an increase in the resistance of the air passage, resulting in a refrigerator with high cooling efficiency. In the refrigerator of the present embodiment, the opening provided in the refrigerating compartment air duct 11 is only the refrigerating compartment discharge opening 11a opened upward, but other openings may be provided in addition to this. In this case, the above-described effect can be obtained by making the opening area (total area) of the discharge opening that opens upward larger than the sum of the opening areas of the other discharge openings.

The refrigerator of the present embodiment is provided with a door basket 33a having an opening position higher than a shelf 34a located at the uppermost layer of the refrigerating room 2, and the refrigerating room discharge opening 11a of the refrigerating room air blowing path 11 provided at the rear surface of the refrigerating room is opened upward (cold air directing means) to blow out air directed upward. As a result, the cooling air flows along the ceiling surface opening position of the refrigerator compartment 2 as shown by the arrow in fig. 2, and the door basket 33a is higher than the shelf 34a located at the uppermost layer of the refrigerator compartment 2, and therefore, the door basket 33a can be cooled well.

In the refrigerator of the present embodiment, the evaporator temperature adjustment means (the compressor 24, the refrigeration blower 9 a) is controlled so that the difference between the refrigerating compartment maintenance temperature (refrigerating compartment set temperature) T _{R_keep} during the steady cooling operation and the refrigerating compartment discharge air temperature T _{R_in} discharged from the refrigerating compartment discharge port 11a is higher than the arithmetic average value of the freezing compartment maintenance temperature T _{F_keep} (refrigerating compartment set temperature) and the refrigerating compartment maintenance temperature (refrigerating compartment set temperature) T _{R_keep}. In general, when low-temperature air is blown into a space having a high temperature, the low-temperature air having a high density receives downward force due to gravity, and therefore, it is difficult for the low-temperature air to reach an area distant from the upper side of the blowout port. Therefore, in the refrigerator of the present embodiment, by controlling the evaporator temperature adjustment means (the compressor 24, the refrigeration blower 9 a) so that the difference between the refrigeration compartment maintenance temperature (refrigeration compartment set temperature) tr_keep and the refrigeration compartment discharge air temperature T _{R_in} is higher than the arithmetic average value of the freezing compartment maintenance temperature tf_keep (refrigeration compartment set temperature) and the refrigeration compartment maintenance temperature (refrigeration compartment set temperature) T _{R_keep}, it is possible to satisfactorily cool the space (for example, the uppermost door basket 33 a) located above the discharge port by the effect of the gravity applied to the cooling air blown out from the refrigeration compartment discharge port 11 a.

The refrigerator of the present embodiment includes a refrigerating chamber 2 (first refrigerating temperature zone chamber), a vegetable chamber 6 (second refrigerating temperature zone chamber), and a freezing chamber 7, a refrigerating evaporator 14a (first evaporator) and a refrigerating fan 9a (first fan) are provided on the back of the refrigerating chamber 2, a freezing evaporator 14b (second evaporator) and a freezing fan 9b (second fan) are provided on the back of the freezing chamber 7, a refrigerating air passage 111 (first air passage) through which cooling air having exchanged heat with the refrigerating evaporator 14a flows into the refrigerating chamber 2 by driving the first fan, and a refrigerating vegetable air passage 112 (second air passage) through which cooling air having exchanged heat with the refrigerating evaporator 14b flows into the freezing chamber 7 and the vegetable chamber 6 by driving the refrigerating fan 9b are provided, and an air flow blocking means (heat-insulating partition wall 28) for blocking the flow of air between the first air passage and the second air passage and a deodorizing member 91 in contact with the air flowing through the refrigerating air passage 111 are provided. Accordingly, when food materials or the like emitting odor are stored in the refrigerator compartment 2, the odor components can be prevented from circulating to other storage compartments (the freezer compartment 7 and the vegetable compartment 6) together with the cooling air, and therefore, odor transfer to the food materials or the like in the storage compartments (the freezer compartment 7 and the vegetable compartment 6) other than the refrigerator compartment 2 can be prevented. In addition, since the cooling air containing the odor component circulates only in the cooling air duct 111 and does not spread to other storage compartments, a high deodorizing effect can be obtained in a shorter time.

The refrigerator of the present embodiment includes a cooling air duct 111 (first air duct), a frozen vegetable air duct 112 (second air duct), and a deodorizing member 91 in contact with air flowing through the cooling air duct 111, and includes an operation mode in which the cooling fan 9a of the cooling chamber 2 is driven for a longer period of time than the cooling fan 9b is driven during a steady cooling operation. Since more air passes through the deodorizing member 91 when the cooling fan 9a is driven, the deodorizing effect is increased, and thus, by providing an operation mode in which the cooling fan 9a is driven for a longer period of time than the cooling fan 9b, a refrigerator having a higher deodorizing effect can be produced.

The refrigerator of the present embodiment includes, from above, a storage chamber in the order of a refrigerating chamber 2 (first refrigerating temperature zone chamber), a freezing chamber 7 (freezing temperature zone chamber), and a vegetable chamber (second refrigerating temperature zone chamber), and includes a freezing evaporator 14b (second evaporator) on the back of the freezing chamber 7, wherein the volume of the freezing evaporator 14b is 3% or less of the rated capacity of the freezing chamber 7, the rated capacity of the freezing chamber 7 is 28% or more of the total rated capacity, and a refrigerating evaporator 14a (first evaporator) on the back of the refrigerating chamber 2 as the refrigerating temperature zone chamber. Thus, a refrigerator having a large-capacity freezing chamber in the central portion of the refrigerator and exhibiting excellent practical cooling performance can be provided. The reason will be described below.

Generally, frost grows on the surface of an evaporator that cools a freezing temperature zone chamber. If frost grows on the surface of the evaporator, the ventilation resistance increases due to the narrowing of the flow path through the evaporator, and the thermal resistance increases due to the frost layer between the evaporator surface and the air, so that the heat exchange performance of the evaporator decreases and the 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. In the defrosting operation in which frost is melted by increasing the temperature of the evaporator by a heating means such as a heater, cooling of the freezing temperature zone chamber cannot be performed. Therefore, if the heat exchange performance of the evaporator is easily degraded by the growth of frost, defrosting operation for raising the temperature of the freezing temperature zone chamber is frequently performed. That is, the problem of stable cooling performance of the freezing temperature zone chamber is to be solved in that the deterioration of heat exchange performance due to the growth of frost is not easily caused. For example, in a refrigerator including a cooler (evaporator) as a heat exchanger for cooling each storage chamber in a cooling chamber (evaporator chamber) at the rear of a freezing chamber as in the refrigerator described in patent document 1, generally, the problem is to be solved by sufficiently increasing the size (evaporator volume) of the evaporator to suppress a decrease in heat exchange performance due to the growth of frost. On the other hand, the volume of the freezing evaporator cannot be set to 3% or less of the rated capacity of the freezing temperature zone chamber, and the rated capacity of the freezing temperature zone chamber cannot be increased to 28% or more of the total rated capacity.

In general, the higher the air temperature is, the more moisture the air contains (the higher the absolute humidity), and therefore, in the case of having an evaporator that commonly cools the freezing temperature zone chamber and the refrigerating temperature zone chamber, more moisture reaches the evaporator from the refrigerating temperature zone chamber whose maintenance temperature is higher than that of the freezing temperature zone chamber, and becomes frost. Therefore, in the refrigerator of the present embodiment, by adopting a configuration in which the freezing evaporator 14b is provided on the back of the freezing chamber 7 and the refrigerating evaporator 14a is provided on the back of the refrigerating chamber 2, even if the evaporator provided on the back of the freezing chamber 7 in the center portion of the refrigerator is miniaturized to 3% or less of the rated capacity of the freezing chamber 7 and the rated capacity of the freezing temperature zone chamber is enlarged to 28% or more of the total rated capacity, the growth of frost due to the moisture from the refrigerating chamber 2 having a large moisture content (absolute humidity) in the air is not generated, and therefore, the evaporator which is difficult to cause a decrease in heat exchange performance is constituted, and stable cooling performance can be exhibited.

Further, the first evaporator is provided in the refrigerating temperature zone chamber having a large rated capacity among the refrigerating chamber 2 and the vegetable chamber 6 serving as refrigerating temperature zone chambers. Accordingly, the refrigerator having both the large-capacity freezing chamber and the good practical cooling performance can be configured because the refrigerating chamber 2, which is liable to be subjected to a large load due to a large capacity, can be cooled efficiently.

In the refrigerator of the present embodiment, the air-side heat transfer area a _Fevp of the refrigeration evaporator 14b is made larger than the air-side heat transfer area a _Revp of the refrigeration evaporator 14 a. In general, when the air-side heat transfer area of the evaporator is increased, heat exchange between air and the refrigerant is promoted, and the cooling capacity increases. Therefore, the air-side heat transfer area a _Fevp of the freezing evaporator 14b is larger than the air-side heat transfer area a _Revp of the refrigerating evaporator 14a, and the cooling capacity of the freezing chamber 7 is further improved, thereby achieving both the large-capacity freezing chamber and the good practical cooling performance.

In the refrigerator of this embodiment, the air-side heat transfer areas per unit volume of the refrigerating evaporator 14a and the freezing evaporator 14b are a _Revp/V_Revp＝0.673m²/L,A_Fevp/V_Fevp＝0.384m²/L, respectively, and are set to a value of 0.25m ²/L or more and 0.96m ²/L or less. Generally, frost grows on the air-side heat transfer surface of the evaporator, and therefore, if the air-side heat transfer area is increased with respect to the volume of the evaporator, the flow path is easily blocked when frost grows. Therefore, an evaporator is configured such that the heat exchange performance is easily reduced when the growth of frost is large, and the heat exchange performance is high when the growth of frost is small. On the other hand, if the air-side heat transfer area is reduced with respect to the evaporator volume, even if frost grows, the flow path is less likely to be blocked by the frost and the heat exchange performance is easily maintained, but if the growth of frost is small, the heat exchange performance per unit volume is reduced. Therefore, in the refrigerator of the present embodiment, the performance of the case where the amount of frost is large and the case where the amount of frost is small can be achieved by setting the air-side heat transfer area per unit volume of the refrigerating evaporator 14a and the freezing evaporator 14b to 0.25m ²/L or more and 0.96m ²/L or less.

The air-side heat transfer area (a _Revp/V_Revp) per unit volume of the refrigeration evaporator 14a is made larger than the air-side heat transfer area (a _Fevp/V_Fevp) per unit volume of the freezing evaporator 14b (a _Revp/V_Revp＞A_Fevp/V_Fevp). The frost grown in the freezing evaporator 14b is melted by the defrosting operation of the freezing evaporator heated by the defrosting heater 21, and the freezing chamber 7 cannot be cooled during the defrosting operation of the freezing evaporator. On the other hand, the frost grown in the refrigeration evaporator 14a can be melted while cooling the refrigeration compartment 2 by the defrosting operation of the refrigeration evaporator. 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 freezing evaporator 14b, the flow path of the freezing evaporator 14b can be made less likely to be blocked by frost, and the cooling of the freezing chamber 7 will not be deteriorated due to the increase in the frequency of the defrosting operation.

In the refrigerator of the present embodiment, when a practical load is placed in both the freezing temperature zone chamber and the refrigerating temperature zone chamber, the evaporator temperature adjustment means (the compressor 24, the refrigerating fan 9a, the refrigerating fan 9b, and the vegetable compartment damper 19) is controlled so that the time average temperature T _{Revp_ave} of the refrigerating evaporator 14a during the refrigerating chamber cooling operation is higher than the time average temperature T _{Fevp_ave} of the refrigerating evaporator 14b during the freezing chamber cooling operation from the time when the load is placed until the practical load is sufficiently cooled. In general, the higher the evaporator temperature (evaporation temperature), the higher the refrigeration cycle coefficient of performance (ratio of the amount of heat absorption 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 set to a low temperature, but the refrigerating chamber 2 needs to be maintained at the refrigerating temperature, and therefore the evaporator temperature adjusting means (the compressor 24, the refrigerating fan 9a, the refrigerating fan 9b, and the vegetable chamber barrier 19) is controlled so that the temperature T _Revp of the refrigerating evaporator is higher than the temperature T _Fevp of the freezing evaporator, thereby improving the energy saving performance.

In the refrigerator of this embodiment, when a practical load is placed on both the freezing temperature zone chamber and the refrigerating temperature zone chamber, the evaporator temperature adjustment means (the compressor 24, the refrigerating fan 9a, the refrigerating fan 9b, and the vegetable chamber damper 19) is controlled so that the maximum value (maximum reached temperature) of the freezing chamber temperature is lower than 0 ℃ (T _F1 <0 in fig. 10). This can prevent the food or the like stored in the freezing temperature zone chamber from being thawed by the placement of the utility load, and can obtain good utility cooling performance.

In the refrigerator of the present embodiment, when a utility load is placed in both the freezing temperature zone chamber and the refrigerating temperature zone chamber, the evaporator temperature adjustment means (the compressor 24, the refrigerating fan 9a, the refrigerating fan 9b, and the vegetable chamber damper 19) are controlled so that the maximum values of the freezing chamber temperature gradually decrease from the time point when the load is placed to the utility load cooling zone where the utility load is sufficiently cooled. Thus, a refrigerator having high practical cooling performance is configured in which a problem of thawing frozen foods due to a temperature rise of a freezing chamber is hardly caused.

In the refrigerator of this embodiment, when a utility load is placed in both the freezing temperature zone chamber and the refrigerating temperature zone chamber, the temperature of the freezing temperature zone chamber is set to R _R, the temperature of the refrigerating chamber is set to R _F, the outside air temperature is set to T _out (C), the air side heat transfer area of the refrigerating evaporator 14a is set to a _Revp(m²), the time average temperature during the refrigerating operation of the refrigerating evaporator 14a is set to T _{Revp_ave} (C), the refrigerating chamber maintenance temperature is set to T _{R_keep} (C), the air side heat transfer area of the refrigerating evaporator 14b is set to a _Fevp(m²), the time average temperature during the freezing chamber cooling operation of the refrigerating evaporator 14b is set to T _{Fevp_ave} (C), the freezing chamber maintenance temperature is set to T _{F_keep} (C), the refrigerating chamber rated capacity is set to V _R (L), the freezing chamber rated capacity is set to V _F (L), the water is set to C25 (kJ/kg), the ice is set to C3438 (kJ/kg), the freezing temperature is set to C37 kg (C), the freezing temperature is set to be 19 kg (j), and the refrigerating temperature is set to A3 kg/3 by a fan, and the refrigerating unit is set to be a cooling fan (3 kg, and the temperature is set by a fan is set to be used, and the freezing temperature is set to be a 6.

Thus, a refrigerator which combines a large capacity freezing chamber and good practical cooling performance is constructed. The reason will be described below. In general, in a refrigerator, not only heat penetration through a wall surface of a heat-insulating box body but also an abnormal load increase occurs in a door opening/closing operation by a user, in the placement of food or the like having a high temperature. In particular, in a refrigerator having a storage compartment with a refrigerating temperature zone and a storage compartment with a freezing temperature zone, even when a large amount of food is simultaneously placed in both storage compartments, the refrigerator needs to be cooled quickly to a predetermined maintenance temperature. However, since the temperature ranges of the refrigerating temperature range chamber and the freezing temperature range chamber are different, there is a possibility that one of the storage chambers is cooled poorly or only one of the storage chambers is excessively cooled. That is, it is an object to cool the refrigerating temperature zone chamber and the freezing temperature zone chamber with good balance. In particular, in a refrigerator including a refrigerating chamber, a freezing chamber, and a vegetable chamber from above, if an evaporator provided on the back of the freezing chamber is miniaturized to 3% or less of the rated capacity of the freezing chamber and the rated capacity of the freezing chamber is increased to 28% or more of the total rated capacity, the balance between the load of the refrigerating chamber and the freezing chamber and the balance between the cooling capacities are impaired, and the problem of poor cooling in one storage chamber or excessive cooling in only one storage chamber is apparent, and thus good cooling performance may not be exhibited. Therefore, in the refrigerator of the present embodiment, when a practical load is placed on the refrigerating chamber 2 and the freezing chamber 7, the freezing operation/the vegetable freezing operation and the refrigerating operation are performed so as to satisfy (expression 3), whereby both the large-capacity freezing chamber and the practical cooling performance are achieved.

A _Fevp×(T_{F_keep}-T_{Fevp_ave} of (formula 3) is an index of the amount of heat exchanged by the refrigeration evaporator 14b, a _Revp×(T_{R_keep}-T_{Revp_ave}) is an index of the amount of heat exchanged by the refrigeration evaporator 14a, 12×v _R×{CW×(T_out-T_{R_keep}) is an index of the amount of heat absorption (cooling load) required for cooling the utility load placed in the refrigerating chamber, and 4×v _F×{C_W×T_out-C_i×T_{F_keep}+L_W is an index of the amount of heat absorption (cooling load) required for cooling the utility load placed in the freezing chamber. That is, the ratio of the freezing chamber cooling operation (freezing chamber wild chamber cooling operation and freezing chamber cooling operation) to the refrigerating chamber cooling operation, which is required to be the minimum of the ratio of the heat exchange amount of the refrigerating evaporator and the freezing evaporator and the ratio of the cooling load of the utility load, is calculated from the right side. In the refrigerator according to the present embodiment, since the freezing chamber cooling operation is controlled so that the ratio is higher, even when a large amount of load is placed on the refrigerating chamber and the freezing chamber at the same time, both the large-capacity freezing chamber and the practical cooling performance can be achieved. The 12 XV _R and 4 XV _F on the right side of (formula 3) are the standard water supply (initial temperature is outside air temperature) of 12g for each 1L of refrigerating temperature zone chamber (refrigerating chamber and vegetable chamber) and the standard water supply (initial temperature is outside air temperature) of 4g for each 1L of freezing temperature zone chamber in the freezing chamber, and the load amount defined by JISC9801-3:2015 is obtained by taking into consideration the general usage method.

Further, since the refrigerator of the present embodiment has an automatic ice making function, it is also assumed that the load fluctuates due to the use of the automatic ice making function by the user. In this case, the ice making water tank is provided in the refrigerating chamber 2, and thus, the load of the refrigerating chamber 2 increases. However, since the freezing is not achieved in the refrigerator compartment 2 maintained in the refrigerating temperature zone, only the sensible heat load is applied, and when water is supplied from the refrigerator compartment 2 to the ice making compartment 3 in the refrigerating temperature zone, the latent heat is also applied as the load in addition to the sensible heat for the freezing. Therefore, since the load of the freezing chamber 7 is increased as compared with the refrigerating chamber 2, the freezing temperature zone chamber is preferably cooled by controlling as shown in (formula 1), and therefore, even when the automatic ice making function is used, the practical cooling performance is easily maintained.

The refrigerating compartment maintenance temperature T _Rkeep and the freezing compartment maintenance temperature T _Fkeep in (formula 1) and (formula 3) may be time-averaged values of the temperatures of the refrigerating compartment 2 and the freezing compartment 7 in the steady cooling operation measured by the method defined by JISC 9801-1:2015. The refrigeration evaporator temperature T _Revp and the refrigeration evaporator temperature T _Fevp used to calculate the time average temperatures (T _{Revp_ave},T_{Fevp_ave}) of the refrigeration evaporator 14a and the refrigeration evaporator 14b may be used by measuring the temperatures in the vicinity of the inflow portions of the refrigerant tubes 97a and 97b of the refrigeration evaporator 14a and the refrigeration evaporator 14 b.

The above is an example showing a mode of carrying out the present invention. The present invention is not limited to the above-described embodiments, and includes various modifications. For example, in the refrigerator of the present embodiment, the heat-insulating partition wall 28 is used as the air flow blocking means for more reliably blocking the flow of air, but a baffle may be provided in a part of the partition member, and the baffle may be closed to block the flow of air. In the refrigerator of the present embodiment, the compressor 24, the refrigerating fan 9a, and the freezing fan 9b are used as the evaporator temperature adjusting means, but as long as the evaporator temperature can be adjusted, a fan for controlling the heat radiation amount of the heat radiation means and an expansion valve capable of changing the throttle resistance may be used as the evaporator temperature adjusting means. That is, the above-described embodiments are embodiments described in detail for easily explaining the present invention, and are not limited to the configuration in which all of the descriptions are necessarily provided.

Claims

1. A refrigerator having a first refrigeration temperature zone chamber, a second refrigeration temperature zone chamber, and a freezing temperature zone chamber, wherein a first evaporator and a first blower are provided on the back of the first refrigeration temperature zone chamber, a second evaporator is provided on the back of the freezing temperature zone chamber, a second blower is provided on the back of the freezing temperature zone chamber or the second refrigeration temperature zone chamber,

The refrigerator is characterized by comprising:

a first air passage configured to circulate the air heat-exchanged with the first evaporator to the first refrigeration temperature zone chamber by driving the first blower; and

A second air passage configured to circulate the air heat-exchanged with the second evaporator to the freezing temperature zone chamber and the second refrigerating temperature zone chamber by driving the second blower,

And an air flow blocking means for blocking the flow of air between the first air passage and the second air passage,

Further comprises a defrosting heater for heating the second evaporator,

A water guide pipe for receiving defrosting water from the first evaporator and a water guide pipe heater for heating the water guide pipe are arranged at the lower part of the first evaporator,

The first air passage circulates the return air from the first refrigerating temperature zone chamber downward toward the water guide pipe and contacts the water guide pipe,

Performing a first evaporator defrosting operation of cooling the first refrigeration temperature zone chamber by using frost growing on a surface of the first evaporator and cold-storage heat of the first evaporator itself and defrosting the first evaporator by setting the first blower to a driving state while the refrigerant does not flow through the first evaporator,

A second evaporator defrosting operation is performed in which the defrosting heater is energized,

The time average temperature of the first evaporator at the time of the refrigerating operation under the steady cooling operation is set to be not less than-1 ℃ as the arithmetic average value of the maintaining temperature of the refrigerating temperature zone chamber and the maintaining temperature of the first refrigerating temperature zone chamber by controlling at least the compressor and the first blower,

At least by controlling the compressor and the first blower, when a difference between a maintenance temperature T _{R_keep} of the first refrigeration temperature zone chamber in the steady cooling operation and a time average temperature T _{Revp_ave} of the first evaporator in the refrigeration operation is set to be DeltaT, deltaT=T _{R_keep}-T_{Revp_ave}, and a coefficient of performance of the refrigeration cycle with respect to the evaporator temperature is set to be COP _th, the following expression is satisfied,

2. A refrigerator comprising a first storage chamber having a refrigerating temperature zone, a second storage chamber having a freezing temperature zone, and a third storage chamber in a heat insulating box, wherein the rated capacity of the first storage chamber is larger than the rated capacity of either the second storage chamber or the third storage chamber,

The above-mentioned refrigerator is characterized in that,

A first evaporator and a first blower are provided in the region dividing the first storage chamber,

A second evaporator and a second blower are provided in a region dividing the second storage chamber or the third storage chamber,

The refrigerator comprises:

a first air passage configured to circulate the air heat-exchanged with the first evaporator to the first storage chamber by driving the first blower; and

A second air passage configured to circulate the air heat-exchanged with the second evaporator to the second storage chamber and the third storage chamber by driving the second blower,

Further comprises a defrosting heater for heating the second evaporator,

The first air passage circulates the return air from the first storage chamber downward toward the water guide pipe and contacts the water guide pipe,

Performing a first evaporator defrosting operation of cooling the first storage chamber by using frost growing on a surface of the first evaporator and cool heat stored in the first evaporator itself and defrosting the first evaporator by setting the first blower to a driving state while the refrigerant does not flow in the first evaporator,

The first blower in the stable cooling operation of the refrigerator in the repeated fixed operation mode is driven for a longer time than the second blower in the stable cooling operation without load fluctuation caused by opening and closing of the storage compartment doors by a user or variation of the temperature environment around the refrigerator,

At least by controlling the compressor and the first blower, when the difference between the maintenance temperature T _{R_keep} of the first refrigeration temperature zone chamber in the steady cooling operation and the time average temperature T _{Revp_ave} of the first evaporator in the refrigeration operation is set to be DeltaT, deltaT=T _{R_keep}-T_{Revp_ave}, and the theoretical coefficient of performance of the refrigeration cycle with respect to the evaporator temperature is set to be COP _th, the following expression is satisfied,

3. A refrigerator having a first storage chamber with a refrigerating temperature zone, a second storage chamber with a freezing temperature zone, and a third storage chamber in a heat insulation box body with a front opening, the refrigerator comprising: a first storage room door body for opening and closing the first storage room; a second storage room door body for opening and closing the second storage room; a third storage room door body for opening and closing the third storage room; a first sealing member that ensures sealing between the first storage compartment door and the heat insulation box; a second sealing member that ensures sealing between the second storage compartment door and the heat insulation box; a third seal member that ensures sealing between the third storage compartment door and the heat insulation box, and has a total circumference that is larger than either the total circumference of the second seal member or the total circumference of the third seal member,

The above-mentioned refrigerator is characterized in that,

The refrigerator comprises:

Further comprises a defrosting heater for heating the second evaporator,