JP5836227B2 - refrigerator - Google Patents

Description

  The present invention relates to a refrigerator.

  As background art in this technical field, there are JP 2012-26677 A (Patent Document 1) and JP 10-54642 A (Patent Document 2).

  In Patent Document 1, a refrigerating room is provided with a rear-side blowing air passage, a ceiling-side blowing air passage, and a twin duct damper for switching the air passage. A refrigerator-freezer is disclosed in which the twin duct damper is controlled based on the temperature detected by the ceiling-side temperature sensor to control the amount of cold air in the refrigerator compartment (Patent Document 1, FIG. 6, etc.).

  Patent Document 2 discloses a refrigerator-freezer in which a temperature detecting means is provided for each location, an open / close damper and a duct for sending cool air for each section, and whether the cool air is sent or not is controlled according to the detected temperature. (Patent Document 2, FIG. 1, etc.).

JP 2012-26677 A JP-A-10-54642

  However, even if it is a refrigerator (refrigeration refrigerator) as described in either patent document 1 and patent document 2, consideration with respect to the structure of an air path is not enough, and cooling efficiency may not become high enough.

  This invention is made | formed in view of the said subject, and it aims at obtaining high cooling efficiency in the refrigerator which switches and cools the air path with respect to a single store room.

In order to solve the above problems, for example, the configuration described in the claims is adopted. The present application includes a plurality of means for solving the above-mentioned problems. To give an example, a storage chamber, a cooler, a blower that blows cold air that exchanges heat with the cooler, and a back surface of the storage chamber. A ventilation path that guides cool air to the storage room, a return path that returns the cool air of the storage room to the cooler, and a vacuum heat insulating material in a rear heat insulating wall of the storage room, the ventilation path and the return path At least one of them has a branch path branched from the path through which the cool air passes, and includes air path resistance control means for controlling the air path resistance of the branch path, and the storage chamber is one of the branch paths. The first independent cooling region cooled by the cold air passing through the path, the second independent cooling region cooled by the cold air passing through the other path of the branch paths, and any one of the branch paths Cooling even by passing cold air And a common cooling area, the minimum flow path cross-sectional area of the one path is greater than the minimum flow path cross-sectional area of the other, upon projecting the branch path to the vacuum heat insulating material side, the branch path At least one of the paths is characterized in that the shortest distance from the outer periphery of the vacuum heat insulating material is 50 mm or more.

  ADVANTAGE OF THE INVENTION According to this invention, high cooling efficiency can be obtained in the refrigerator which switches and cools the air path with respect to a single store room.

The front external view of the refrigerator which concerns on 1st embodiment of this invention. The longitudinal cross-sectional view showing the structure in the store | warehouse | chamber of the refrigerator which concerns on 1st embodiment of this invention. The front view showing the structure of the refrigerator compartment of the refrigerator which concerns on 1st embodiment of this invention. The schematic diagram which shows the cold air circulation path | route of the refrigerator which concerns on 1st embodiment of this invention. The figure showing the internal fan of the refrigerator which concerns on 1st embodiment of this invention. The figure showing the refrigerator compartment damper of the refrigerator which concerns on 1st embodiment of this invention. The figure showing the vacuum heat insulating material of the refrigerator which concerns on 1st embodiment of this invention. The figure showing the mounting state of the vacuum heat insulating material of the refrigerator which concerns on 1st embodiment of this invention. The figure showing the combination of the damper opened / closed state of the refrigerator which concerns on 1st embodiment of this invention. Explanatory drawing of the characteristic and operating point of the air blower of the refrigerator which concerns on 1st embodiment of this invention. Explanatory drawing of the blowing flow of the air blower of the refrigerator which concerns on 1st embodiment of this invention. The flowchart showing control of the refrigerator which concerns on 1st embodiment of this invention. The figure which shows the air volume measuring method of the refrigerator which concerns on embodiment of this invention. The longitudinal cross-sectional view showing the structure in the store | warehouse | chamber of the refrigerator which concerns on 2nd embodiment of this invention. The front view showing the structure of the refrigerator compartment of the refrigerator which concerns on 2nd embodiment of this invention. The schematic diagram which shows the cool air circulation path | route of the refrigerator which concerns on 2nd embodiment of this invention. The longitudinal cross-sectional view showing the structure in the store | warehouse | chamber of the refrigerator which concerns on 3rd embodiment of this invention. The front view showing the structure of the refrigerator compartment of the refrigerator which concerns on 3rd embodiment of this invention. The schematic diagram which shows the cold air circulation path | route of the refrigerator which concerns on 3rd embodiment of this invention. The figure showing the combination of the damper open / close state of the refrigerator which concerns on 3rd embodiment of this invention.

  A first embodiment of a refrigerator according to the present invention will be described with reference to FIGS.

  FIG. 1 is a front outline view of the refrigerator of the present embodiment. FIG. 2 is a vertical cross-sectional view showing the configuration inside the refrigerator of the present embodiment. FIG. 3 is a front view illustrating the configuration of the refrigerator compartment of the refrigerator according to the present embodiment. FIG. 4 is a schematic diagram showing the air path configuration of the refrigerator of the present embodiment. FIG. 5 is a diagram illustrating the internal fan of the refrigerator according to the present embodiment. FIG. 6 is a diagram illustrating the freezer damper of the refrigerator according to the present embodiment.

  As shown in FIG. 1, the refrigerator main body 1 of the present embodiment includes a refrigerator compartment 2, an ice making compartment 4, an upper freezer compartment 5, a lower freezer compartment 6, and a vegetable compartment 8 from above. The ice making chamber 4 and the upper freezer compartment 5 are provided side by side between the refrigerator compartment 2 and the lower freezer compartment 6. The refrigerator compartment 2 and the vegetable compartment 8 are storage rooms in a refrigerator temperature zone of about 5 ° C. as an example. In addition, the ice making room 4, the upper freezing room 5, and the lower freezing room 6 are storage rooms having a freezing temperature range of about −18 ° C. to −20 ° C. as an example (hereinafter referred to as the ice making room 4, the upper freezing room 5, and the lower freezing room). The general name of the chamber 6 is referred to as a freezing chamber 7).

  The refrigerating room 2 is provided with double door-type refrigerating room doors 2a and 2b that are divided into left and right on the front side. The ice making room 4, the upper freezing room 5, the lower freezing room 6, and the vegetable room 8 are each provided with a drawer type ice making room door 4a, an upper freezing room door 5a, a lower freezing room door 6a, and a vegetable room door 8a.

  As shown in FIG. 2, the outside of the refrigerator and the inside of the refrigerator of the present embodiment are formed by filling a foam insulation (foamed polyurethane) between the outer box 1a and the inner box 1b. Separated by. Moreover, the refrigerator of this embodiment has mounted the vacuum heat insulating material 60 on the back surface (the mounting state of the vacuum heat insulating material 60 will be described later).

  A plurality of door pockets 47a to 47c are provided on the storage room side of the refrigerator compartment doors 2a and 2b. The refrigerator compartment 2 includes a plurality of shelves 46a to 46f (see FIG. 3 for shelves 46a and 46d).

  In addition, the ice making room 4, the upper freezing room 5, the lower freezing room 6, and the vegetable room 8 are storage containers 4b that move in the front-rear direction integrally with doors 4a, 5a, 6a, 8a provided in front of the respective storage rooms. 5b, 6b, 8b. Each of the doors 4a, 5a, 6a, and 8a is configured so that the storage containers 4b, 5b, 6b, and 8b can be pulled out by putting a hand on a handle portion (not shown) and pulling it out to the front side.

  As shown in FIG. 2, the refrigerator of the present embodiment includes a refrigerator compartment 2, an upper freezer compartment 5, and an ice making chamber 4 (see FIG. 1) that are adiabatically separated by an upper heat insulating partition wall 51. The vegetable compartment 8 is adiabatically separated by the lower heat insulating partition wall 52. In addition, between the shelf 46f and the upper side heat insulation partition wall 51, the chilled chamber 3 maintained at about -1 to 1 degreeC is provided as an example. Therefore, in the refrigerator of this embodiment, the area | region except the chilled room 3 maintained at low temperature among the storage areas above the upper side heat insulation partition wall 51 becomes a storage room of a refrigeration temperature zone. In addition, it is good also as a reduced pressure storage chamber which maintains the chilled chamber 3 in a pressure-reduced state and suppresses the oxidation of food.

  As shown in FIG. 2, the refrigerator of the present embodiment includes an evaporator storage chamber 9 at the back of the freezer compartment 7, and an evaporator 21 (as an example, a fin tube type heat exchange) as a cooling means in the evaporator storage chamber 9. Equipment). Further, above the evaporator 21, an internal fan 22 is provided as a blowing means.

As shown in FIG. 5, the internal fan 22 of the refrigerator of the present embodiment is an axial fan (propeller fan) that drives a blade 91 having an outer diameter of 110 mm by a motor (not shown) in a central motor housing portion 92. ). The motor housing portion 92 is connected to the housing 94 by a support portion 93. The blowing area (π × [0.5 × blade outer diameter] ² ) is 9503.3 mm ² as an example.

Further, as shown in FIG. 2, a defrost heater 56 is provided below the evaporator storage chamber 9. The frost that has grown on the wall of the evaporator 21 and the surrounding evaporator storage chamber 9 is solved by the defrosting operation in which the defrosting heater 56 is energized. The defrost water generated by the melting of the frost flows into the eaves 57 provided at the lower part of the evaporator storage chamber 9 and then reaches the evaporating dish 59 disposed in the machine chamber 10 through the drain pipe 58. The defrost water in the evaporating dish 59 evaporates due to heat generated by the compressor 23 and the condenser (not shown) disposed in the machine room 10.
The refrigerator according to the present embodiment includes a compressor 23 disposed in the machine room 10, a condenser (for example, a finned tube heat exchanger), and an outer box between the outer box 1a and the inner box 1b. A heat radiating pipe (not shown) disposed so as to be in contact with the surface 1a and a dew condensation suppressing pipe (not illustrated) disposed on the front surface of the upper heat insulating partition wall 51 or the front surface of the lower heat insulating partition wall 52 of the heat insulating box 10 (Not shown), a dryer (not shown) for drying and absorbing moisture in the refrigerant, a capillary tube (not shown), and the evaporator 21 are sequentially connected by a refrigerant pipe to constitute a refrigeration cycle. Yes. The refrigerant is isobutane.

As shown in FIG. 3, the back surface of the refrigerator compartment 2 is provided with the refrigerator compartment 1st ventilation duct 11a and the refrigerator compartment 2nd ventilation duct 11b which are extended toward upper direction from the downward direction in the approximate center. The refrigerating room first air duct 11a on the left side of the refrigerating room 2 is a refrigerating room that blows out cold air to a region 2d (see FIGS. 2 and 3) below the uppermost shelves 46a and 46b and above the lowermost shelves 46f. The blowout ports 31a to 31c are provided. The opening area of the refrigerating compartment outlet 31a is open area of 1000 mm ^2, the refrigerating chamber outlet 31b is 500 mm @ 2, the opening area of the refrigerating compartment outlet 31c is 200 mm ^2. Moreover, the refrigerator compartment 2nd ventilation duct 11b on the left side back of the refrigerator compartment 2 is provided with refrigerator compartment outlets 31d and 31e that blow out into the region 2c (see FIGS. 2 and 3) above the shelves 46a and 46b. The opening area of the refrigerating compartment outlet 31d is an opening area of 500 mm ^2, 31e is 500 mm ^2. The minimum flow path cross-sectional area of the first blower duct 11a and the refrigerating compartment the second air duct 11b refrigerating chamber, respectively 1640Mm ² and 1110mm ^2.

  Incidentally, the height of the shelves 46a to 46e can be changed within a predetermined range (the shelf 46f is fixed). Therefore, although the sizes of the region 2c and the region 2d change, the variable ranges of the shelf 46a and the shelf 46b are the distances from the shelf 46a and the shelf 46b to the upper wall (the height H1 and the height shown in FIG. 3). H2) is made smaller than the respective depth dimensions of the shelf 46a and the shelf 46b. The volume of the area 2c in the state where the installation height of the shelves 46a and 46b is the lowest is 50L, the volume of the area 2d is 140L, and the volume of the area 2e in which the door pockets 47b and 47c and the ice making water tank 55 are installed is 40L.

The refrigerating room damper 24 (air path resistance control means) for controlling the air blowing to the refrigerating room 2 is provided in the rear projection region of the upper heat insulating partition wall 51 as shown in FIG. Thereby, the damper can be mounted while suppressing the reduction of the food storage space.
As shown in FIG. 6, the refrigerator compartment damper 24 includes openings 82 a and 82 b on the left and right sides of the motor storage portion 81. Opening 82a and opening 82b are opened and closed by opening and closing plates 83a and 83b. Specifically, the open / close plates 83a and 83b are each in a range from a fully closed state with an open angle of 0 degrees to a fully open state with an open angle of 90 degrees by a stepping motor (not shown) installed in the motor storage unit 81. It can be controlled. Hereinafter, of the functions of the refrigerator compartment damper 24, the function of controlling the open / close state of the opening 82a is referred to as the refrigerator compartment first damper 24a, and the function of controlling the open / close state of the opening 82b is referred to as the refrigerator compartment second damper 24b.

  As shown in FIG. 3, the refrigerator compartment first damper 24a and the refrigerator compartment second damper 24b are provided at the inlets of the refrigerator compartment first air duct 11a and the refrigerator compartment second air duct 11b, respectively. The ventilation to the 1 ventilation duct 11a and the refrigerator compartment 2nd ventilation duct 11b is controlled.

  As shown in FIGS. 2 and 3, a refrigerator compartment first temperature sensor 41 a (mainly detecting the load of the area 2 d) is provided on the back of the area partitioned by the bottom shelf 46 f and the second shelf 46 d from the bottom. Temperature detecting means). The upper wall of the refrigerating chamber 2 is provided with a refrigerating chamber second temperature sensor 41b (temperature detecting means) that mainly detects the load in the region 2c. Furthermore, a chilled chamber temperature sensor 42 (temperature detecting means) is provided on the back of the region partitioned by the shelf 46f and the upper heat insulating partition wall 51 (the back of the chilled chamber 3). Note that the refrigeration room first temperature sensor 41a, the refrigeration room second temperature sensor 41b, and the chilled room temperature sensor 42 are installed in a place where cold air having a relatively high flow rate is not directly applied to improve detection accuracy.

  Moreover, the freezer compartment temperature sensor 43 and the vegetable compartment temperature sensor 44 are each provided in the back part of the freezer compartment 7 and the back part of the vegetable compartment 8 (refer FIG. 2).

  An ice making water tank 55 for storing ice making water is provided at the left end of the area defined by the shelf 46f and the upper heat insulating partition wall 51. The water in the ice making water tank 55 is supplied to an ice making tray (not shown) provided in the ice making chamber 4 through a pipe (not shown) by driving a pump (not shown).

  FIG. 7 is a diagram illustrating a vacuum heat insulating material mounted on the refrigerator of the present embodiment. FIG. 8 is a view (an enlarged view in the vicinity of the region A in FIG. 2) showing a mounting state of the vacuum heat insulating material.

  As shown in FIG. 7, the vacuum heat insulating material 60 is formed by compressing and sealing a core material 61 (glass wool as an example) together with an adsorbent 62 (synthetic zeolite as an example), and inside an outer packaging material 64 (a laminated film including an aluminum vapor deposited film layer). After evacuation, the end is thermally welded. Therefore, although the heat welding part 60a shown in FIG. 7 exists in the edge part of a vacuum heat insulating material, in the refrigerator of this embodiment, as shown in FIG. 8, the heat welding part 60a is shown inside a warehouse (foaming heat insulating material side). After being folded back and fixed, a foam heat insulating material is filled between the inner box 1b and the outer box 1a to form the heat insulating box 50. Accordingly, the vacuum heat insulating material 60 has a folded portion 60b formed by folding the heat welding portion 60a on the outer periphery. In this embodiment, the vacuum heat insulating material 60 is attached to the inner surface of the outer box 1a with an adhesive such as hot melt, but this is not restrictive. For example, the structure affixed on the inner surface of the inner box 1b or the structure disposed on the inner box 1b and the outer box 1a via a support member may be used. Fold it back on the foam insulation side).

  If the core material 61 is stored in the inner bag 63 (for example, polyethylene) and stored in the outer packaging material 64 in a temporarily compressed state, then the inner bag 63 and the outer packaging material 64 are compressed and sealed. The handleability of the material 61 is improved, and the manufacturing process can be made efficient.

As shown by a broken line in FIG. 3, the vacuum heat insulating material 60 is mounted in the rear heat insulating wall of the refrigerator, but has the above-described folded portion 60 b (region surrounded by the inner broken line and the outer broken line) on the outer periphery. .
In the refrigerator according to the present embodiment, as shown in FIG. 3, when the refrigerator compartment first air duct 11 a is projected onto the rear vacuum insulator 60, the end of the vacuum insulator 60 from the refrigerator compartment first fan duct 11 a end. The shortest distance L to reach 100 mm. Moreover, the refrigerator compartment 1st ventilation duct 11a is made to fit inside the folding | returning part 60b of the vacuum heat insulating material 60. FIG. Thereby, it can suppress that the influence by what is called a heat bridge phenomenon in which heat is transmitted through the metal layer in the outer packaging material 64 of the vacuum heat insulating material 60 does not reach the refrigerator compartment 1st ventilation duct 11a. Details will be described later.

  Next, the cold air circulation path of the refrigerator of this embodiment will be described with reference to FIG. 4 and FIGS. 2 and 3 as appropriate.

As shown in FIG. 4, the cold air exchanged with the evaporator 21 is pressurized by the internal fan 22 and flows through the refrigerating chamber first air duct 11a in the open state of the refrigerating chamber first damper 24a so as to return to the refrigerating chamber outlet. It blows out from 31a-31c to the area | region 2d (refer FIG.2 and FIG.3) in a refrigerator compartment. The cold air blown out into the region 2d flows through the region 2e (see FIGS. 2 and 3) where the door pockets 47b and 47c and the ice making water tank 55 are installed, through the chilled chamber 3, and reaches the refrigerating chamber return port 35. On the other hand, when the refrigerating room second damper 24b is open, the refrigerating room second air duct 11b flows through the refrigerating room outlet 31d, 31e and blows out to the area 2c in the refrigerating room (see FIGS. 2 and 3).
The cold air blown out into the area 2c flows through the area 2e (see FIGS. 2 and 3) where the door pockets 47b and 47c and the ice making water tank 55 are installed, through the chilled chamber 3, and reaches the refrigerating room return port 35.

The cold air that has cooled the regions 2c, 2d, and 2e and the chilled chamber 3 enters the refrigerating chamber return duct 15 (for example, the minimum flow passage cross-sectional area of 1700 mm ² ) from the refrigerating chamber return port 35, reaches the evaporator storage chamber 9, and evaporates again. Heat exchange with the vessel 21.
Next, in the open state of the freezer damper 26, the cold air boosted by the internal fan 22 flows through the freezer air blower duct 13 and blows out from the freezer outlets 33a to 33c (see FIG. 2) to the freezer compartment 7. The cold air that has cooled the freezer compartment 7 returns to the evaporator storage chamber 9 from the freezer return port 36 and exchanges heat with the evaporator 21 again.

  When the vegetable compartment damper 27 is in an open state, the cold air boosted by the internal fan 22 flows through the vegetable compartment air duct 14 and blows out from the vegetable compartment outlet 34 to the vegetable compartment 8. The cold air that has cooled the vegetable compartment 8 enters the vegetable compartment return duct 17 from the vegetable compartment return port 37, reaches the evaporator storage chamber 9, and exchanges heat with the evaporator 21 again.

  Next, the characteristics of the internal fan of the refrigerator of the present embodiment and the air path resistance of each internal air path will be described with reference to FIGS.

  FIG. 9 is a diagram showing combinations of damper open / close states, and FIG. 10 is a diagram showing the relationship between the air flow-static pressure characteristics of the internal fan 22 and the operating point. FIG. 11 is a schematic diagram showing the flow of air blown out from the internal fan 22.

  The air path resistance of the cold air circulation path varies depending on the open / close state of the damper. The refrigerator according to the present embodiment includes a refrigerator compartment first damper 24a, a refrigerator compartment second damper 24b, a freezer compartment damper 26, and a vegetable compartment damper 27, each of which takes two states: an open state and a closed state. There are 16 combinations of open / close states. FIG. 9 shows a combination in which at least one of the refrigerator compartment first damper 24a or the refrigerator compartment second damper 24b is in an open state and air is sent to the refrigerator compartment 2.

  As shown in FIG. 9, there are twelve states, state 1 to state 12, in which ventilation to the refrigerator compartment 2 is performed, and the air path resistance of the cold air circulation path in each state is R <b> 1 to R <b> 12. In the “air path resistance magnitude” column, numbers 1 to 12 are assigned to R1 to R12 in ascending order of the air path resistance. That is, the magnitude relationship between R1 to R12 is “R6 <R12 <R4 <R10 <R5 <R11 <R3 <R9 <R1 <R7 <R2 <R8”.

  FIG. 10 is a diagram showing the air volume-static pressure characteristics of the internal fan 22 and the operating points when the states 1 to 6 shown in FIG. 9 are set.

  As shown in FIG. 10, the air volume-static pressure characteristics of the internal fan 22 have a maximum point at which the gradient turns from rising to falling on the large air volume side, and a minimum point at which the gradient turns from falling to rising on the small air volume side. This is a characteristic found in a general axial fan. When the air volume is decreased from the open point where the static pressure is zero, a stall occurs in which the flow is separated from the blades when the predetermined air volume is reached. The point where stall occurs is called the stall point, and the maximum point of the airflow-static pressure characteristic is generally regarded as the stall point. When the air volume is decreased from the stall point, a region where the static pressure decreases (rising region to the right) appears, and after reaching the minimum point, the static pressure rises again by centrifugal action and reaches the closing point where the air volume is zero. On the large air volume side from the open point to the maximum point, as shown by the arrow in FIG. 11 (a), the air blown out from the internal fan 22 flows in the axial direction, from the minimum point to the cut-off point. On the small air volume side, the air blown out from the internal fan 22 flows in the radial direction (centrifugal direction) and flows as indicated by arrows in FIG. Therefore, hereinafter, the range from the open point to the maximum point will be referred to as the “axial flow region”, the range from the maximum point to the minimum point will be referred to as the “right upward characteristic range”, and the range from the minimum point to the cut-off point will be referred to as “centrifugal flow range”.

  The intersection between the resistance curves of the resistors R1 to R6 in the states 1 to 6 shown in FIG. 10 and the air volume-static pressure characteristic curve of the internal fan 22 is an operating point in each state. Therefore, the air volume when each damper is in the state 1 to the state 6 is Q1 to Q6 shown in FIG. 10, and any operating point is a centrifugal flow region. Further, the magnitude relationship between the air volumes is “Q6> Q4> Q5> Q3> Q1> Q2.” Incidentally, although omitted in FIG. 10, the magnitude of the air volume is shown as Q 7 to Q 12 with the air volumes of the resistors R 7 to R 12 as “Q 6> Q 12> Q 4> Q 10> Q 5> Q 11> Q 3> Q 9> Q 1> Q 7. > Q2> Q8 ”. That is, the air volume tends to increase in ascending order of the wind path resistance in each state.

  The refrigerator of the present embodiment includes a temperature setter (not shown) for setting the temperature of the refrigerator compartment 2, the chilled compartment 3, the freezer compartment 7 and the vegetable compartment 8, and the upper rear of the upper wall of the refrigerator body 1. On the side, a control board 49 on which a CPU, a memory such as a ROM and a RAM, an interface circuit and the like are mounted is disposed (see FIG. 2). The control board 49 includes the refrigeration room first temperature sensor 41a, the refrigeration room second temperature sensor 41b, the chilled room temperature sensor 42, the freezer room temperature sensor 43, the vegetable room temperature sensor 44, and the refrigeration room door 2a and the inside of the refrigerator. Connected to a temperature setter or the like provided in

  ON / OFF of compressor 23, control of each actuator (not shown) which operates refrigerator compartment damper 24, freezer compartment damper 26, and vegetable compartment damper 27, ON / OFF control and rotation speed control of internal fan 22 Further, control such as ON / OFF of an alarm for notifying the door open state is performed by a program previously installed in the ROM, and a control device is configured by these.

  Next, control of the refrigerator of this embodiment will be described with reference to FIG.

  FIG. 12 is a control flowchart showing control during the cooling operation of the refrigerator of the present embodiment. In the refrigerator of the present embodiment, the compressor 23 is driven by turning on the power and the cooling operation is started (start). Here, the control state until the inside of the refrigerator is sufficiently cooled is omitted, and the description is started from the time when the interior of the refrigerator is sufficiently cooled and the condition for driving the compressor 23 is satisfied from the state where the compressor 23 is stopped. . When the driving conditions of the compressor 23 are satisfied (the driving conditions of the compressor 23 will be described later), the compressor 23 and the internal fan 22 are driven (step S101), and the opening condition of the refrigerator compartment first damper 24a is established. It is determined whether or not (step S102). In the refrigerator of the present embodiment, the open condition of the refrigerator compartment first damper 24a is “the compressor 23 is stopped, the temperature detected by the refrigerator compartment first temperature sensor 41a is equal to or higher than Tr1_a (Tr1_a = 3 ° C. in the refrigerator of this embodiment)” Or “the compressor 23 is driven, the freezer damper 26 is closed, and the temperature detected by the first temperature sensor 41a is not less than Tr1_a”, or “the compressor 23 is driven, the freezer damper 26 is open, This is established when the detected temperature of the one temperature sensor 41a is equal to or higher than Tr1_b (Tr1_b = 7 ° C. in the refrigerator of the present embodiment). When step S102 is established (Yes), the refrigerator compartment first damper 24a is opened (step S103), and cold air is sent to the region 2d (see FIG. 2 or FIG. 3) in the refrigerator compartment 2.

  Subsequently, it is determined whether or not the condition for opening the second refrigerator 24b is satisfied (step S104). In the refrigerator of this embodiment, the open condition of the refrigerator second damper 24b is “the compressor 23 is stopped, the temperature detected by the refrigerator second temperature sensor 41b is equal to or higher than Tr2_a (Tr2_a = 4 ° C. in the refrigerator of this embodiment)”. Or “compressor 23 drive state, freezer compartment damper 26 closed state, second temperature sensor 41b detection temperature of the refrigerator compartment is Tr2_a or higher” or “compressor 23 drive state, freezer compartment damper 26 open state, refrigerator compartment first state” This is established when the temperature detected by the two-temperature sensor 41b is equal to or higher than Tr2_b (Tr2_b = 8 ° C. in the refrigerator of the present embodiment). When step S104 is established (Yes), the refrigerating chamber second damper 24b is opened (step S105), and the cool air is sent to the region 2c in the refrigerating chamber 2 (see FIG. 2 or FIG. 3).

  Next, it is determined whether or not the closing condition for the refrigerator compartment first damper 24a is satisfied (step S106). In the refrigerator of this embodiment, the closing condition of the refrigerator compartment first damper 24a is “the temperature detected by the refrigerator compartment first temperature sensor 41a is equal to or lower than Tr1_c (Tr1_c = 2 ° C. in the refrigerator of this embodiment)” or “chilled chamber This is established when the temperature detected by the temperature sensor 42 is equal to or lower than Tc_a (Tc_a = −1 ° C. in the refrigerator of the present embodiment). When step S106 is established (Yes), the refrigerator compartment first damper 24a is closed (step S107).

  Subsequently, it is determined whether or not a condition for closing the second refrigerator 24b is satisfied (step S108). In the refrigerator of the present embodiment, the refrigerating chamber second damper 24b is closed under the condition that “the temperature detected by the second refrigerator temperature sensor 41b is Tr2_c or less (Tr2_c = 3 ° C. in the refrigerator of the present embodiment)” or “chilled chamber This holds true when the temperature detected by the temperature sensor 42 is Tc_a or less. When step S108 is established (Yes), the refrigerator second damper 24b is closed (step S109).

  Next, it is determined whether or not a condition for opening the freezer damper 26 is satisfied (step S110). In the refrigerator of the present embodiment, the open condition of the freezer compartment damper 26 is “compressor 23 drive state, refrigerator compartment first damper 24a closed state, refrigerator compartment second damper 24b closed state”, or “compressor drive state, This is established when the temperature detected by the freezer temperature sensor 43 is equal to or higher than Tf_a (Tf_a = −14 ° C. in the refrigerator of the present embodiment) ”. When step S110 is established (Yes), the freezer compartment damper 26 is opened and cold air is sent to the freezer compartment 7 (step S111).

  Subsequently, it is determined whether a stop condition for the internal fan 22 is satisfied (step S112). In the refrigerator of the present embodiment, the stop condition of the internal fan 22 is established when the compressor 23 is stopped, the refrigerator compartment first damper 24a is closed, and the refrigerator compartment second damper 24b is closed. When step S112 is established (Yes), the internal fan 22 is stopped.

  Next, it is determined whether a stop condition for the compressor 23 is satisfied (step S114). In the refrigerator of this embodiment, the stop condition of the compressor 23 is established when “the temperature detected by the freezer temperature sensor 43 is equal to or lower than Tf_b (Tf_b = −20 ° C. in the refrigerator of this embodiment)”. When step S114 is not established (No), the process returns to the determination of step S102 again.

  When Step S114 is established (Yes), the compressor 23 is stopped and the freezer damper 26 is closed (Step S115). Subsequently, it is determined whether or not the driving condition of the compressor 23 is satisfied (step S116). In the refrigerator of the present embodiment, the driving condition of the compressor 23 is established when “the temperature detected by the freezer temperature sensor 43 is Tf_c or higher (Tf_c = −16 ° C. in the refrigerator of the present embodiment)”. When step S116 is not established (No), the process returns to the determination of step S102 again. Moreover, when step S116 is materialized (Yes), the compressor 23 and the internal ventilation 22 are driven by step S101, and the process proceeds to step S102.

  In the above control flow, the description of the operation of the vegetable compartment damper 26 is omitted. However, in the refrigerator of the present embodiment, the vegetable compartment damper 26 opens the refrigerator compartment first damper 24a or the refrigerator compartment second damper 24b. And is closed when the temperature detected by the vegetable room temperature sensor 44 is lower than the lower limit temperature Tv (Tv = 3 ° C. in the refrigerator of the present embodiment).

  Although the structure of the refrigerator of this embodiment was demonstrated above, the effect which the refrigerator of this embodiment plays is demonstrated below.

  In the refrigerator of the present embodiment, when at least one of the refrigerator compartment first damper 24a or the refrigerator compartment second damper 24b is in an open state, the operating point is smaller than the minimum point in the air volume-static pressure characteristics of the internal fan 22. (Refer to FIG. 10). Thereby, a refrigerator with high cooling efficiency can be provided. The reason will be explained below.

  The refrigerator of the present embodiment includes an independent refrigeration chamber first air duct 11a and a second refrigeration chamber second air duct 11b as air passages to the refrigerator compartment 2, and is mainly cooled by the refrigerator compartment first air duct 11a. The region 2d is provided with a refrigerating chamber first temperature sensor 41a for detecting the temperature, and a region 2c cooled mainly by the refrigerating chamber second air duct 11b is provided with a refrigerating chamber second temperature sensor 42b. Based on the detected temperatures of the refrigerator compartment first temperature sensor 41a and the refrigerator compartment second temperature sensor 42b, the open / close state of the refrigerator compartment first damper 24a and refrigerator compartment second damper 24b is controlled (see FIG. 12). As a result, the region 2c and the region 2d (see FIG. 2 or 3) in the refrigerator compartment 2 are cooled in a short time if the air flow rate is excessive, and if the air flow rate is too small, the cooling time is Although it extends, it can be reliably cooled to a predetermined value. That is, with respect to the region 2c and the region 2d, a cooling state with high efficiency can be obtained because there is no excessive or insufficient cooling regardless of the air flow rate. On the other hand, the region 2e through which the cold air passes in common regardless of whether the first refrigerator 24a or the second refrigerator 24b is opened is either the first refrigerator 24a or the second refrigerator 24b. However, since it will be cooled if it is in the open state, it is not possible to suppress over- and under-cooling by switching the blowing state. For example, when the air flow rate to the region 2e becomes excessive, the region 2c or the region 2d is sufficiently cooled when the region 2c or the region 2d is sufficiently cooled, and when the air flow rate becomes excessively small, the region 2c or the region 2d is sufficient. At the time of cooling, the region 2e is in a state of insufficient cooling. In particular, when the ice making water tank 55 is provided in the area 2e through which the cold air passes in common as in the refrigerator of the present embodiment, when the area 2e is excessively cooled, the water in the ice making water tank 55 is frozen. There is. Therefore, since heating with a heater or the like is required to prevent freezing in the ice making water tank 55, the heat load increases correspondingly, and the cooling efficiency is lowered.

  Therefore, the air path resistance and the warehouse of the cold air circulation path in a state in which the refrigerator compartment first damper 24a and the refrigerator compartment second damper 24b are opened so that the air flow rate that can cool the region 2e through which the cold air passes in common can be obtained without excess or deficiency. It is required to adjust the rotational speed of the inner blower 22.

  In general, if the operating point determined by the air volume-static pressure characteristics and the air path resistance (resistance curve in FIG. 10) of the internal fan is stable, the air flow is proportional to the rotational speed of the internal fan, so the rotational speed is The air flow can be easily adjusted by changing.

  On the other hand, when the operating point changes greatly, the relationship between the rotational speed of the internal fan and the air flow rate changes, and it becomes difficult to obtain a predetermined air flow rate. In a conventional refrigerator (for example, the refrigerator described in Patent Document 1 or Patent Document 2), the operating point of the cold air circulation path may change greatly for the reasons described below, and the accompanying decrease in cooling efficiency is a problem. It was.

  An axial blower is a blower generally used in an axial flow region (see FIG. 10) on the larger air volume side than the stall point. Therefore, for comparison, first, a case will be described in which the air path is configured so that the operating point becomes an axial flow region while suppressing the air path resistance of the cold air circulation path to be small.

  In the refrigerator, since frost grows in the evaporator during the cooling operation, it is inevitable that the air path resistance gradually increases as the frost grows. At this time, if the air path resistance is kept small in order to set the operating point as the axial flow region, the increase degree of the air path resistance due to the frost grown on the evaporator increases, and the operating point increases with the growth of the frost. Changes to the small air volume side. Accordingly, even if either the refrigerator compartment first damper 24a or the refrigerator compartment second damper 24b is in an open state, the amount of air blown to the region 2e through which the cold air passes is greatly changed, leading to a reduction in cooling efficiency.

  Therefore, as in the refrigerator of the present embodiment, when the air path resistance is relatively large and the air path is configured so that the operating point is in the centrifugal flow region, the air path resistance that is the base even if frost grows. Is relatively large, the degree of increase in wind path resistance due to frost growth is relatively small. Accordingly, since the degree of decrease in the air volume becomes small, it is possible to suppress a decrease in the cooling efficiency of the region 2e through which the cold air passes in common regardless of which of the refrigerator compartment first damper 24a and the refrigerator compartment second damper 24b is opened.

  Moreover, the operation | movement to the right rising characteristic area between an axial flow area and a centrifugal flow area may become unstable. Therefore, in general, it is desirable to avoid it in order to obtain a stable air flow rate, but when the air passage is configured so that the operating point is an axial flow region, the air passage resistance increases as frost grows, When the operating point enters the rising characteristic area, there may be a situation where a stable air flow rate to the area 2e cannot be obtained.

  Therefore, as in the refrigerator of the present embodiment, if the operating point is in the centrifugal flow region, even if the air path resistance increases with the growth of frost, the degree of decrease in the air volume can be kept small, and the operation Therefore, it is also possible to avoid the region 2e through which the cold air passes in common regardless of whether the first refrigerator 24a or the second refrigerator 24b is opened. It becomes a refrigerator with high cooling efficiency that can be cooled without shortage.

  In addition, what is necessary is just to discriminate | determine that an operating point exists in a centrifugal flow area as follows, for example.

  First, the air volume-static pressure characteristic of the internal fan is measured according to JISB 8330: 2000. Next, the air volume of the refrigerator is measured. FIG. 13 is a schematic diagram showing a state in which the amount of air flowing through the refrigerator compartment return port 35 of the refrigerator of this embodiment is being measured.

  As shown in FIG. 13, the refrigerator compartment doors 2a and 2b are opened so that the duct 100 covers the refrigerator compartment return port 35, and the pressure difference between the internal pressure of the duct 100 and the external pressure (atmospheric pressure). A first differential pressure gauge 103 for measuring the pressure, an orifice 102 capable of calculating an air volume based on the differential pressure on the upstream side and the downstream side, a second differential pressure gauge 104 for measuring the differential pressure on the upstream side and the downstream side of the orifice 102, The air volume is measured using an air volume measuring device constituted by the blower 101 on the upstream side of the orifice. Specifically, adjusting the blower 101 so that the differential pressure of the first differential pressure gauge 103 becomes zero, and measuring the amount of air flowing through the refrigerating chamber return port 35 based on the second differential pressure gauge 104 at that time. it can. In addition, although the refrigerator compartment doors 2a and 2b are in an open state, since the differential pressure of the first differential pressure gauge is adjusted to be zero, the state is almost the same as the state in which the refrigerator compartment doors 2a and 2b are closed. It can be considered. Incidentally, the air volume blown out from the outlet can also be measured by reversing the orifice 102 and the blower 101 from the installation state shown in FIG. 13 and sucking out the air in the duct 100. For example, if the duct 100 is installed so as to guide the air from the outlets 31a to 31c of the refrigerator compartment first air duct 11a and the blower 101 is adjusted so that the differential pressure of the first differential pressure gauge 103 becomes zero, Based on the differential pressure of the second differential pressure gauge 104, the amount of air blown from the refrigerator compartment first air duct 11a can also be measured. Although an example of the air volume measurement method using the throttle mechanism has been described here, the air volume may be measured using other means such as a thermal flow meter.

  With the above method, the air volume-static pressure characteristics of the blower alone and the operating air volume of the refrigerator are clarified. From both, it is possible to determine whether the operating point is in the centrifugal flow region with sufficient accuracy in practice. it can.

  In addition, in the single unit performance of an axial-flow fan, when the local maximum point and local minimum point do not appear clearly, it can confirm that it is a centrifugal flow area as follows.

  In the axial blower, generally, the flow blows out in the axial direction in the axial flow region, and the flow blows out in the radial direction in the centrifugal flow region (see FIG. 11). Therefore, in the case of a blower having an air volume-static pressure characteristic in which the maximum point and the minimum point do not appear clearly, the axial flow region and the centrifugal flow region can be distinguished from each other by the change in the blowing flow. Specifically, as shown in FIG. 11, a virtual surface (conical surface) inclined 45 degrees from the front of the front edge 91a of the outer periphery of the blade of the axial blower 22 is considered, and the inner side (front) of the surface is the front region, When the flow is blown out to the front region with the outside of the surface as the radial region, it is determined that the operating point is in the axial flow region, and when the flow is blown out in the radial region, it is determined that the operating point is in the centrifugal flow region. Therefore, for example, when the wind speed on the meridian plane at a certain distance from the front edge 91a of the blade outer periphery is measured together with the measurement of the air volume-static pressure characteristics of the blower alone, and the point indicating the maximum value of the wind speed enters the forward region What is necessary is just to determine with a centrifugal flow area, when entering into an axial flow area and a radial direction area | region. Incidentally, the wind speed blown out from the blower has an axial component, a radial (centrifugal) component, and a circumferential component. Therefore, for example, when measured with an omnidirectional anemometer, the wind speed in which these components are combined is measured, but the axial flow is relatively small, and the centrifugal flow region where the radial flow is formed It is possible to determine that the

  The refrigerator of the present embodiment includes a vacuum heat insulating material 60 in the rear heat insulating wall, and when the refrigerator compartment first air duct 11a is projected onto the rear vacuum heat insulator 60, a vacuum is applied from the end of the refrigerator compartment first air duct 11a. The shortest distance L to the end of the heat insulating material 60 is set to be 50 mm or more (L = 100 mm in the refrigerator of this embodiment). In this state, an operation mode is implemented in which the refrigerator compartment first damper 24a that sends air to the refrigerator compartment first air duct 11a is opened, and the refrigerator compartment second damper 24b that sends air to the refrigerator compartment second air duct 12a is closed. (See FIGS. 3 and 12). Thereby, a refrigerator with high cooling efficiency can be provided. The reason will be explained below.

  Like the vacuum heat insulating material 60 (see FIG. 7) of the refrigerator of the present embodiment, it is covered with an outer packaging material including a metal layer having a high thermal conductivity (a laminate film including an aluminum deposited film layer in the refrigerator of the present embodiment). The region of less than 50 mm from the outer periphery of the vacuum heat insulating material becomes a so-called heat bridge region in which the heat insulating performance is lowered because a large amount of heat moves through the outer packaging material. Therefore, if a duct is provided in front of the heat bridge region, heat loss increases and cooling efficiency decreases. Therefore, it is desirable to take care not to dispose a duct in front of the heat bridge region. However, in order to satisfactorily cool the inside of the refrigerator compartment, it is necessary to guide the cold air to the predetermined position with a duct. In particular, in order to reliably deliver cold air to the region above the refrigerator compartment (region 2c in the refrigerator of the present embodiment) where the cold air is difficult to reach due to natural convection, it is necessary to arrange the duct up to the upper portion of the refrigerator compartment. Along with this, a duct is disposed in front of the heat bridge region.

  So, in the refrigerator of this embodiment, when the refrigerator compartment 1st ventilation duct 11a is projected on the vacuum insulation material 60 of the back, the shortest distance from the edge part of the refrigerator compartment 1st ventilation duct 11a to the edge part of the vacuum insulation material 60 L is separated by 50 mm or more, and the refrigerator compartment first air duct 11a is made as a highly insulated air passage with small heat loss, and air is sent to the refrigerator compartment first air duct 11a in a state where it is not necessary to cool the region 2c. By implementing the operation mode in which the refrigerator compartment first damper 24a is in the open state and the refrigerator compartment second damper 24b for blowing air to the refrigerator compartment second air duct 12a is in the closed state, the cooling efficiency that suppresses heat loss due to the heat bridge is achieved. It becomes a high refrigerator.

  Moreover, when the vacuum heat insulating material 60 is provided in the back heat insulating wall and the refrigerating chamber first air duct 11a is projected onto the rear vacuum heat insulating material 60, the refrigerating chamber second is formed in the area inside the folded portion 60b of the vacuum heat insulating material 60. It is configured so that one air duct 11a can be accommodated, the refrigerating room first damper 24a for blowing air to the refrigerating room first air duct 11a is opened, and the refrigerating room second damper 24b for air blowing to the refrigerating room second air duct 12a is closed. The operation mode to be set is performed (see FIGS. 2, 3, 8, and 12). The folded portion of the vacuum heat insulating material is greatly affected by the heat bridge because the outer packaging material overlaps. Therefore, in the refrigerator of the present embodiment, by adopting the above-described configuration, the cooling operation that suppresses the heat loss due to the heat bridge caused by the folded portion 60b is performed, so that the refrigerating chamber first air duct 11a has a small heat loss. Cooling efficiency is improved as a highly insulated air passage.

  Moreover, the refrigerator compartment 2nd ventilation duct 11b which ventilates the area | region 2c above the uppermost shelf 46a, 46b, and the refrigerator compartment 1st ventilation duct 11a which ventilates the area | region 2d below the uppermost shelf 46a, 46b is provided. Then, an operation mode is implemented in which the refrigerator compartment first damper 24a that sends air to the refrigerator compartment first air duct 11a is opened, and the refrigerator compartment second damper 24b that sends air to the refrigerator compartment second air duct 12a is closed (FIG. 2). FIG. 3 and FIG. 12). Thereby, in a state where it is not necessary to cool the region 2c, the air layer in the region 2c above the uppermost shelves 46a and 46b suppresses the heat effect from the upper wall of the refrigerator compartment 2 from reaching the region 2d. Therefore, efficient cooling is possible.

  Further, the respective distances (H1 and H2 shown in FIG. 3) from the shelf 46a and the shelf 46b to the upper wall are made smaller than the respective depth dimensions of the shelf 46a and the shelf 46b. As a result, an operation mode in which the refrigerator compartment first damper 24a for blowing air to the refrigerator compartment first air duct 11a is opened and the refrigerator compartment second damper 24b for sending air to the refrigerator compartment second air duct 12a is closed is performed. When the air layer in the region 2c is caused to act as a heat insulating layer, convection in the region 2c is hardly generated, so that the heat insulating effect by the region 2c is enhanced and more efficient cooling is possible.

  In addition, the volume of the region through which the cold air passes in common (the volume of the region 2e) regardless of which of the refrigerator compartment first damper 24a and the refrigerator compartment second damper 24b is in the open state is the refrigerator compartment first damper 24a and the refrigerator compartment second. The volume is made smaller than the volume of the area where the air flow is controlled independently by the open / close state of the damper 24b (the volume of the area 2c and the area 2d). Thereby, even if an operating point changes to a small air volume side with the growth of frost, it can suppress that the influence of the fall of cooling efficiency appears notably.

  Moreover, the minimum flow path cross-sectional area of the refrigerator compartment 1st ventilation duct 11a and the refrigerator compartment 2nd ventilation duct 11b is made smaller than the blowing area of the fan 22 in a store | warehouse | chamber. Thereby, the air path resistance of the cold air circulation system path of the refrigerator compartment 2 is made large, suppressing the duct occupation volume. Therefore, it becomes a refrigerator with high cooling efficiency and space efficiency.

  Moreover, the minimum flow path cross-sectional area of the refrigerator compartment return duct 15 is made smaller than the blowing area of the internal fan 22. Thereby, the air path resistance of the cold air circulation system path of the refrigerator compartment 2 is increased while suppressing the duct occupation volume. Therefore, it becomes a refrigerator with high cooling efficiency and space efficiency.

  Moreover, the minimum flow path cross-sectional area of the refrigerator compartment 1st ventilation duct 11a is made larger than the minimum flow path cross-sectional area of the refrigerator compartment 2nd ventilation duct 11b. As a result, when both the refrigerator compartment first damper 24a and the refrigerator compartment second damper 24b are opened, a large amount of cold air flows through the refrigerator compartment first air duct 11a, which is a highly insulated air passage. A cooling operation with high cooling efficiency can be performed.

  Also, a path (region 2e, chilled chamber 3, refrigerator compartment return port 35, refrigerator compartment return) through which the cold air blown from the refrigerator compartment first air duct 11a and the cold air blown from the refrigerator compartment second air duct 11b flow in common. The duct 15) is provided with a temperature sensor (chilled chamber temperature sensor 42), and when the sensor detection temperature drops below a predetermined temperature (Tc_a or less), the refrigerator compartment first damper 24a that sends air to the refrigerator compartment first air duct 11a. All of the refrigerator compartment second dampers 24b that send air to the refrigerator compartment second air duct 12a are in a closed state (see FIGS. 2, 3, 4, and 12). Thereby, the area | region (The area | region 2e and the chilled room 3 in the refrigerator compartment of the refrigerator of this embodiment) cooled in common by the ventilation from the refrigerator compartment 1st ventilation duct 11a and the refrigerator compartment 2nd ventilation duct 11b is excessively cooled. The problem of freezing can be avoided.

  In the refrigerator of the present embodiment, since the chilled chamber 3 can be cooled to a predetermined temperature without having a cold air outlet, the chilled chamber 3 does not have an outlet that blows out into the chilled chamber. The chilled chamber second air duct 11b may be provided with a chilled chamber outlet. Moreover, it is good also as a structure which is equipped with the chilled chamber damper for controlling the ventilation from a chilled chamber blowing outlet, and is easy to maintain at predetermined temperature.

  A second embodiment of the refrigerator according to the present invention will be described with reference to FIGS. FIG. 14 is a longitudinal section showing the configuration of the refrigerator compartment of the refrigerator of the second embodiment. FIG. 15 is a front view illustrating the configuration of the refrigerator compartment of the refrigerator according to the second embodiment. FIG. 16 is a schematic diagram showing the air path configuration of the refrigerator of the second embodiment. In addition, since it is the same as that of the refrigerator of 1st embodiment except the structure shown in FIGS. 14-16, description is abbreviate | omitted. Moreover, in FIGS. 14-16, about the same functional component as the refrigerator of 1st embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted.

The refrigerator of this embodiment is provided with a refrigerator compartment air duct 11 (minimum channel cross-sectional area of 1700 mm ² ) that extends upward from below on the back of the refrigerator compartment 2 (see FIGS. 14 and 15). The refrigerator compartment air duct 11 is provided with refrigerator compartment outlets 31a to 31c (see FIG. 14). A refrigerator compartment first return duct 15a (minimum channel cross-sectional area 1640 mm ² ) is disposed adjacent to the right side of the refrigerator compartment air duct 11. Return ports 35a and 35b are provided in the upper part of the refrigerator compartment first return duct 15a. In addition, a refrigeration chamber second return duct 15b (minimum channel cross-sectional area and 1400 mm ² ) is provided on the rear surface of the chilled chamber, and a return port 35c is provided in the refrigeration chamber second return duct 15b (FIG. 15). reference). The inflow of the return cold air to the refrigerator compartment first return duct 15a and the refrigerator compartment second return duct 15b is caused by the refrigerator compartment first damper 24a and the refrigerator compartment second damper disposed in the rear projection region of the upper heat insulating partition wall 51. It is controlled by the open / closed state of 24b (see FIG. 15).

  Next, with reference to FIG. 16 and FIGS. 14 and 15 as appropriate, a circulation path of cold air for cooling the refrigerator compartment of the refrigerator of the present embodiment will be described.

  As shown in FIG. 16, the cold air exchanged with the evaporator 21 is boosted by the internal fan 22, and flows in the refrigerating room air duct 11 in the open state of the refrigerating room first damper 24 a to refrigerating room outlets 31 a to 31-. From 31c, it blows out to the area | region 2d (refer FIG.14 and FIG.15) below the uppermost shelf 46a, 46b in the refrigerator compartment, and upper than the lowermost shelf 46f. The cold air blown out into the region 2d flows through the region 2e (see FIG. 14) where the door pocket 47b is installed, returns to the refrigerator compartment through the region 2c (see FIGS. 14 and 15) above the shelves 46a and 46b. It reaches the mouths 35a and 35b (see FIG. 15). The cold air flowing into the refrigerator compartment first return duct 15a (see FIG. 15) from the refrigerator compartment return ports 35a and 35b (see FIG. 15) returns to the evaporator storage chamber 9 and exchanges heat with the evaporator 21 again.

  Moreover, in the open state of the refrigerator compartment second damper 24b, the cold air flows through the refrigerator compartment air duct 11 and blows out from the refrigerator compartment outlets 31a to 31c to the region 2d. The cold air blown out into the region 2d flows through the region 2e, passes through the region 2f (see FIGS. 14 and 15) where the door pocket 47c and the ice making water tank 55 are installed, cools the chilled chamber 3, and returns to the refrigerator compartment. It reaches the mouth 35c (see FIG. 15). The cold air that has flowed into the refrigerator second return duct 15b (see FIG. 15) from the refrigerator return port 35c returns to the evaporator storage chamber 9 and exchanges heat with the evaporator 21 again.

  Moreover, in the refrigerator of this embodiment, when the refrigerator compartment air duct 11 is projected on the back vacuum heat insulating material 60 as shown in FIG. 15, it reaches from the refrigerator compartment air duct 11 end part to the vacuum heat insulating material 60 end part. The shortest distance L is 100 mm. Moreover, the refrigerator compartment 1st ventilation duct 11a is settled inside the folding | returning part 60b of the vacuum heat insulating material 60. FIG.

  As described above, the refrigerator of the present embodiment includes the refrigerator compartment air duct 11, the refrigerator compartment first return duct 15a, and the refrigerator compartment second return duct 15b. When projected onto 60, the shortest distance L from the end of the refrigerating chamber blower duct 11 to the end of the vacuum heat insulating material 60 is set to 50 mm or more. Further, when the refrigerator compartment air duct 11 is projected onto the rear vacuum heat insulating material 60, the refrigerator compartment air duct is accommodated in a region inside the folded portion 60 b of the vacuum heat insulating material 60. Thereby, it can be set as the refrigerator with high cooling efficiency by arrange | positioning the refrigerator compartment air duct 11 into which the cool air of a low temperature flows in the position which suppressed the heat loss by a heat bridge.

  Moreover, in the refrigerator of this embodiment, it can be made to control ventilation to the ice-making water tank 55 installation part periphery (area | region 2f) by the opening / closing state of the refrigerator compartment 2nd damper 24b. That is, the ice making water tank 55 is not installed in a region (regions 2d and 2f) through which cold air passes in common regardless of which of the first refrigerator 24a and the second refrigerator 24b is open. As a result, the periphery of the ice making water tank 55 is hardly cooled excessively, and heating by a heater or the like for preventing water in the ice making water tank 55 from being frozen can be suppressed, so that a refrigerator with high cooling efficiency is obtained.

  A third embodiment of the refrigerator according to the present invention will be described with reference to FIGS. FIG. 17 is a longitudinal cross-sectional view illustrating the configuration of the refrigerator according to the third embodiment, FIG. 18 is a front view illustrating the configuration of the refrigerator compartment of the refrigerator according to the third embodiment, and FIG. 19 illustrates the wind of the refrigerator according to the third embodiment. It is a schematic diagram showing a road configuration. Moreover, FIG. 20 is a figure showing the combination of the open / closed state of the damper of the refrigerator of 3rd embodiment. In addition, in FIGS. 17-20, about the same functional component as the refrigerator of 1st embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted.

As shown in FIG. 18, the refrigerator of the present embodiment includes a refrigerator compartment first air duct 11 a extending from the lower side of the refrigerator compartment 2 to the upper side and a refrigerator compartment first fan duct 11 a ( on top of the minimum flow path cross-sectional area 1400 mm ²⁾ comprises a refrigerating chamber second air duct 11b (minimum flow path cross-sectional area 1400 mm ^2), the refrigerating compartment inlet of the first blower duct 11a and the refrigerating compartment the second air duct 11b Each has a refrigerator compartment first damper 24a and a refrigerator compartment second damper 24b. 17 and 18, the refrigerator compartment first damper 24a is disposed in the rear projection area of the upper heat insulating partition wall 51, and the refrigerator compartment second damper 24b and the refrigerator compartment shelf 46 are refrigerated. The chamber first damper 24b is disposed substantially on the back of the shelf 46a (when the height of the shelf 46a is at the lower end).

  Next, the cold air circulation path of the refrigerator of the present embodiment will be described with reference to FIG. 19 and FIGS. 17 and 18 as appropriate.

  As shown in FIG. 19, the cold air exchanged with the evaporator 21 is boosted by the internal fan 22, and the refrigerator compartment first damper 24 a is in the open state and the refrigerator compartment second damper 24 b is in the closed state. It flows through one ventilation duct 11a, and blows off only to the area | region 2d (refer FIG.17 and FIG.18) in a refrigerator compartment from the refrigerator compartment outlet 31a-31c (refer FIG.18). The cold air blown out into the region 2d flows through the region 2e (see FIG. 17) where the door pockets 47b and 47c are installed, the chilled chamber 3, and reaches the refrigerating chamber return port 35. When the refrigerator compartment first damper 24a is in the open state and the refrigerator compartment second damper 24b is in the open state, the cold air flows through the refrigerator compartment first air duct 11a and enters the region 2d from the refrigerator compartment outlets 31a to 31c. While blowing out, it flows through the refrigerator compartment 2nd ventilation duct 11b, and blows off from the refrigerator compartment outlet 31d and 31e to the area | region 2c (refer FIG.17 and FIG.18) in a refrigerator compartment. The cold air blown out into the region 2c flows through the region 2e where the door pockets 47b and 47c and the ice making water tank 55 are installed, the chilled chamber 3, and reaches the refrigerating chamber return port 35.

The cold air that has cooled the regions 2c, 2d, and 2e and the chilled chamber 3 enters the refrigerating chamber return duct 15 (minimum channel cross-sectional area 1700 mm ² ) from the refrigerating chamber return port 35, reaches the evaporator storage chamber 9, and again reaches the evaporator 21. Exchange heat with.

  In addition, the refrigerator of this embodiment is also provided with a refrigerator compartment first damper 24a, a refrigerator compartment second damper 24b, a freezer compartment damper 26, and a vegetable compartment damper 27, each taking two states, an open state and a closed state. Therefore, there are 16 combinations of damper open / close states, but since the refrigerator second damper 24b is located downstream of the refrigerator first damper 24a, the refrigerator compartment is only in the case where the refrigerator first damper 24a is open. The 2nd damper 24b is open | released and ventilation can be performed through the refrigerator compartment 2nd ventilation duct 11b.

FIG. 20 shows a combination in which the refrigeration chamber first damper 24a is in an open state and the refrigeration chamber 2 is blown. As shown in FIG. 20, there are eight states, state 1 to state 8, where air is blown into the refrigerator compartment 2, and the air path resistance of the cold air circulation path in each state is R1 to R8. In the “air path resistance magnitude” column, numbers 1 to 8 are assigned to R1 to R8 in ascending order of the air path resistance. That is, the magnitude relationship between R1 to R8 is “R4 <R8 <R3 <R7 <R2 <R6 <R1 <R5”. In the refrigerator of this embodiment, the operating point determined by the intersection of the resistance curves of the resistors R1 to R8 in the states 1 to 8 and the air volume-static pressure characteristic curve of the internal fan 22 is a centrifugal flow region.
As described above, in the refrigerator of the present embodiment, since the refrigerator compartment second damper 24b is located downstream of the refrigerator compartment first damper 24a, it is necessary to provide the refrigerator compartment first air duct 11a and the refrigerator compartment second air duct 11b. Disappears. Therefore, since the refrigerator compartment air duct can be arranged in a compact manner, the refrigerator has a reduced food storage space.

  As mentioned above, each Example of this invention can have the following effects.

  That is, the storage room (the refrigeration room 2 and the chilled room 3), the cooler 21, the axial blower 22 that blows the cold air heat-exchanged with the cooler 21, and the cold air blown by the axial blower 22 to the storage room And a return path 15 for returning the cool air blown into the storage chamber to the cooler 21, and at least one of the blow path 11 and the return path 15 is a branch path (a path through which the cool air passes is branched ( The first air duct 11a and the second air duct 11b) are provided with air passage resistance control means 24 for controlling the air passage resistance of the branch path, and the storage room is one of the branch paths. The first independent cooling region 2d cooled by the cold air passing through the (refrigeration room first air duct 11a) and the cold air passing through the other of the branch paths (the cold room second air duct 11b). Second independent cooling Area 2c and common cooling area 2e cooled by the cold air passing through any of the branch paths, and any of first independent cooling area 2d, second independent cooling area 2c, and common cooling area 2e One or a plurality of air blowing modes for cooling in combination, and in any of the plurality of air blowing modes, the axial blower 22 has an operating point on the small air volume side from the minimum point of the air volume-static pressure characteristic curve. Control to be.

  As a result, since the degree of decrease in the air volume is reduced, the cold air passes in common in any of a plurality of air blowing modes (either the first refrigerator 24a or the second refrigerator 24b is opened). A decrease in the cooling efficiency of the region 2e can be suppressed.

  In addition, not only the refrigerator compartment 2 and the chilled room 3 but the above structure is applied also to other storage rooms, and similarly high cooling efficiency can be obtained.

  In addition, the storage room (the refrigeration room 2 and the chilled room 3), the cooler 21, the axial blower 22 that blows the cold air heat-exchanged with the cooler 21, and the cold air blown by the axial blower 22 to the storage room And a return path 15 for returning the cool air blown into the storage chamber to the cooler 21, and at least one of the blow path 11 and the return path 15 is a branch path (a path through which the cool air passes is branched ( The first air duct 11a and the second air duct 11b) are provided with air passage resistance control means 24 for controlling the air passage resistance of the branch path, and the storage room is one of the branch paths. The first independent cooling region 2d cooled by the cold air passing through the (refrigeration room first air duct 11a) and the cold air passing through the other of the branch paths (the cold room second air duct 11b). Second independent cooling zone c and a common cooling region 2e that is cooled by the cold air passing through any of the branch paths, and any one of the first independent cooling region 2d, the second independent cooling region 2c, and the common cooling region 2e It has a plurality of air blowing modes that cool by combining one or a plurality, and in any case of the plurality of air blowing modes, the blowout flow of the axial flow fan 22 is set as an operating point that becomes a centrifugal flow region.

  As a result, if the operating point is in the centrifugal flow region, even if the wind path resistance increases with the growth of frost, the degree of decrease in the air volume can be kept small, and the operation may become unstable. Since it is also possible to avoid entering into the upwardly rising characteristic region, the cold air passes in common in any of a plurality of air blowing modes (whichever of the refrigerator compartment first damper 24a and the refrigerator compartment second damper 24b is opened). A refrigerator with high cooling efficiency capable of cooling the region 2e without excess or deficiency.

  Further, the volume of the common cooling region 2e is made smaller than the volumes of the first independent cooling region 2d and the second independent cooling region 2c. Thereby, even if an operating point changes to a small air volume side with the growth of frost, it can suppress that the influence of the fall of cooling efficiency appears notably.

  Further, the temperature detection means 42 is provided in the area of the return path 15 through which the cold air flows in common in any of the common cooling area 2e and the plurality of air blowing modes, and the temperature detected by the temperature detection means 42 becomes a predetermined temperature or less. If this happens, stop blowing to the storage room. Thereby, it can prevent that the area | region of the return path | route 15 into which cold air | flow flows in common in any case of the common cooling area | region 2e or a some ventilation mode can be prevented from being overcooled and frozen, and cooling efficiency can be improved.

In addition, this invention is not limited to each above-mentioned Example, Various modifications are included. For example, if the operating point determined by the airflow-static pressure characteristics and the airflow resistance of the axial flow fan is a centrifugal flow region, the airway configuration may be determined based on the airflow-static pressure characteristics of the axial flow fan used, After determining the air path configuration, an axial blower whose operating point is the centrifugal flow region may be designed or selected. Alternatively, when a combination of damper open / close states where the operating point is not in the centrifugal flow region occurs, control is performed so as to avoid the use of the combination, or the damper is set in a half-open state (for example, an open angle of 45 °), The operating point in the ascending characteristic range may be adjusted to be the centrifugal flow range.
Moreover, you may increase the division | segmentation number of a ventilation duct or a return duct. As the temperature detection means, a known temperature sensor such as a thermistor, a thermocouple, a semiconductor temperature sensor, a digital temperature sensor, an analog temperature sensor, or the like can be applied. Also, it has a means for detecting stored items such as an optical sensor and an infrared sensor, and controls the opening and closing of the damper and the ventilation based on these by combining the arrangement of the detected stored items and the detected temperature of the temperature detecting means. It is good.
That is, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.

1 refrigerator body 2 refrigerator compartment 2c area (second independent cooling area)
2d region (first independent cooling region)
2e area (common cooling area)
3 Chilled room 7 Freezer room 9 Evaporator storage room 11 Refrigeration room air duct (air flow path)
11a Refrigeration room first air duct (branch route)
11b Refrigerating room second air duct (branch route)
15 Refrigerating room return duct (return path)
21 Evaporator (cooler)
22 Internal fan (axial fan)
24 Cold room damper (wind resistance control means)
24a refrigerator compartment first damper 24b refrigerator compartment second damper 31 refrigerator compartment outlet 35 refrigerator compartment return port 41a refrigerator compartment first temperature sensor (temperature detection means)
41b Second temperature sensor in the refrigerator compartment (temperature detection means)
42 Chilled chamber temperature sensor (temperature detection means)
46 Shelf 47 Door pocket 49 Control board 50 Heat insulation box 51 Upper heat insulation partition wall (partition)
52 Lower heat insulation partition wall (partition)
55 Ice making water tank 60 Vacuum insulation

Claims (2)

A storage chamber, a cooler, a blower that blows cool air heat-exchanged with the cooler, a ventilation path that guides cool air from the back of the storage chamber to the storage chamber, and returns the cool air in the storage chamber to the cooler A return path and a vacuum heat insulating material in the rear heat insulating wall of the storage room,
At least one of the air blowing path and the return path has a branch path in which a path through which cool air passes is branched,
Air path resistance control means for controlling the air path resistance of the branch path;
The storage chamber is cooled by cold air passing through one of the branch paths and cooled by cold air passing through the other of the branch paths, and a second independent cooling region cooled by cold air passing through the other path of the branch paths. An independent cooling region, and a common cooling region that is cooled by cold air passing through any of the branch paths,
The minimum channel cross-sectional area of the one path is larger than the other minimum channel cross-sectional area,
Upon projecting the branch path to the vacuum heat insulating material side, refrigerator wherein at least said one path branch path, characterized in that the shortest distance between the outer periphery of the vacuum heat insulating material was made to separated at least 50 mm. A storage chamber, a cooler, a blower that blows cool air heat-exchanged with the cooler, a ventilation path that guides cool air from the back of the storage chamber to the storage chamber, and returns the cool air in the storage chamber to the cooler A return path and a vacuum heat insulating material in the rear heat insulating wall of the storage room,
At least one of the air blowing path and the return path has a branch path in which a path through which cool air passes is branched,
Air path resistance control means for controlling the air path resistance of the branch path;
The storage chamber is cooled by cold air passing through one of the branch paths and cooled by cold air passing through the other of the branch paths, and a second independent cooling region cooled by cold air passing through the other path of the branch paths. An independent cooling region, and a common cooling region that is cooled by cold air passing through any of the branch paths,
The minimum channel cross-sectional area of the one path is larger than the other minimum channel cross-sectional area,
Upon projecting the branch path to the vacuum heat insulating material side, at least the one path of the branch path refrigerator is characterized in that to fit the inside of the folded portion of the vacuum heat insulating material.