WO2015035863A1

WO2015035863A1 - Refrigerator

Info

Publication number: WO2015035863A1
Application number: PCT/CN2014/085742
Authority: WO
Inventors: 大汤英树; 青木均史; 町田典正; 馆野恭也; 山口龙彦
Original assignee: 海尔亚洲国际株式会社; 青岛海尔股份有限公司
Priority date: 2013-09-10
Filing date: 2014-09-02
Publication date: 2015-03-19
Also published as: JP2015055376A; JP6344895B2

Abstract

A refrigerator with a shielding apparatus that reliably prevent defrosting hot air from leaking. The movable shielding apparatus (50) is arranged on an outer side of an air supply outlet (13a) of a cooling chamber (13). The shielding apparatus (50) is used for shutting the air supply outlet (13a). Specifically, the shielding apparatus (50) mainly comprises: an air supply hood (51) that is approximately in a cover shape and a support base (52) that supports the air supply hood (51). A main function of the shielding apparatus (50) is to shut an opening part of the cooling chamber (13) during a defrosting operation, thus suppressing hot air generated during defrosting from leaking to an air supply path.

Description

Refrigerator

The present invention relates to a refrigerator for cooling and storing foods and the like in a storage compartment, and more particularly to a refrigerator capable of preventing hot air from entering a storage compartment during a defrosting operation. Background technique

In a general refrigerator, when the defrosting of the cooler is performed, there is a problem that the hot airflow around the cooler heated by the defrosting heater enters the storage compartment to raise the temperature in the storage compartment. Therefore, as a method of preventing hot air from entering the storage compartment in the defrosting operation, a known method is to provide a damper in the cooling air passage and close the damper in the defrosting operation (for example, Patent Document 1).

Fig. 7 is a front view showing the air passage structure of the refrigerator 100 disclosed in Patent Document 1. In the refrigerator 100 of the prior art, inlet dampers 105, 106, 107, and 108 are provided in the cold air supply passages 101, 102, 103, and 104 for supplying cold air cooled by the cooler to the storage compartment, respectively. Further, outlet dampers 113, 114, 115 are provided in the cool air return air passages 109, 110, 111 from which the cold air is returned from the storage compartment to the cooler portion. Further, an outlet damper 116 is provided in a cool air return air passage (not shown) from the freezing compartment 112. Moreover, in the defrosting operation, all or a part of the inlet dampers 105, 106, 107, 108 and the outlet dampers 113, 114, 115, 116 are closed.

Further, as another example of the prior art, as shown in FIGS. 8(A) and 8(B), a known technique is to provide the blowers 205, 305 in the cold air outlet to the storage compartment, and The air volume control mechanisms 200 and 300 are provided in the blowers 205 and 305 (for example, Patent Document 2).

The air volume control mechanism 200 of the prior art shown in Fig. 8 (A) is an air-side outer frame to which the axial flow fan 205 is attached to one side of the plurality of opening and closing plates 201, and is connected by a small connection via the connecting plate 202 and the rotating plate 203. The motor 204 is driven to open and close the opening and closing plate 201.

Further, in the air volume control mechanism 300 shown in Fig. 8(B), a windshield shutter 301 is provided on the suction side of the axial flow fan 305. The windshield shutter 301 is opened and closed by a solenoid 304 connected via a operation plate 302 and a connecting shaft 303.

The prior art documents cited herein are as follows:

Patent Document 1: Japanese Patent Publication No. JP 2009-250476 (page 4-5, Fig. 4); Patent Document 2: Japanese Patent Publication No. JP 2006-300427 (pages 7-8, Figs. 3 and 5). However, as shown in FIG. 7, in those prior art refrigerators in which a damper is provided in a cooling air passage, For various refrigerators designed to have different capacities and functions, it is necessary to design respective wind paths and dampers corresponding to the air passages for each model. Therefore, if a damper suitable for the air passage of each model is provided, the type of the damper will increase, and it will become a multi-variety and small-batch production method, so there is a problem that the development cost of the damper and the production cost increase.

In addition, for the method of installing the damper in the cooling air passage, there is a problem that the air passage of the damper installation portion is narrowed, and the flow resistance of the damper itself is also increased, so the pressure loss of the cooling air is increased. . In particular, when a design for reducing the number of dampers is employed, it is necessary to concentrate the cooling air passage to the damper portion, so that the air passage loss at the damper portion becomes very large.

Further, as shown in Fig. 8(A), in the configuration in which the air volume control mechanism 200 is attached to the air blower 205, there is a problem that the air flow control mechanism 200 has a large flow resistance. BP, when the flow of the air on the air side of the axial flow fan forms a swirling flow centering on the vicinity of the rotating shaft of the fan, since the air volume limiting mechanism 200 has a structure in which a plurality of opening and closing plates 201 are arranged in parallel, the rotation is hindered. flow.

Further, when the windshield shutter 301 shown in Fig. 8(B) is used for the air outlet side of the blower, there is a problem that the pressure loss of the blower outlet portion is large. In other words, when the air flow on the air outlet side of the blower in the refrigerator has a characteristic that the flow velocity in the direction of the radial direction is larger than the flow velocity in the direction of the rotation axis of the fan, the windshield shutter 301 blocks the flow in the direction of the radius of rotation. Summary of the invention

The present invention has been made in view of the above problems, and an object thereof is to provide a refrigerator which can reliably prevent hot air from entering a storage chamber during defrosting, reduce pressure loss of a cooling air passage, and improve cooling efficiency.

The refrigerator of the present invention comprises: a storage compartment; a cooling chamber formed with an air supply opening portion and a return air opening portion respectively connected to the storage chamber; a cooler disposed inside the cooling chamber, facing the return air The air flowing in the opening is cooled; the blower is provided in the air blowing opening; the defrosting mechanism defrosts the cooling chamber; and the shielding device closes the air blowing opening from the outside of the cooling chamber The shielding device has a blower cover that closes the air supply opening portion, and a support base disposed between the blower and the blower cover, the blower cover is closed when the air supply opening is closed The support base abuts.

According to the present invention, the movable blower cover is provided outside the air blowing opening portion of the cooling chamber to close the air blowing opening portion by the blower cover in the defrosting operation, so that it is not necessary to provide the damper in the cooling air passage. Therefore, it is possible to prevent the hot air flow during defrosting from entering the storage compartment.

In addition, the blower cover of the present invention can move away from the cooling chamber, so the cooling air The flow loss is very small. Therefore, it is possible to allow the air having a large flow velocity in the direction of the radial direction of the blower side of the blower to flow into the cooling air passage through the opening portion with a small flow resistance. Therefore, the pressure loss of the cooling air circulating in the refrigerator can be reduced, and the cooling efficiency can be improved.

Further, since the refrigerator of the present invention blocks the flow of the defroster hot air only at the outlet portion of the cooling chamber, the number of the seal portions is smaller than that of the prior art method using a plurality of dampers, and a reliable seal with less leakage can be realized.

Further, in the present invention, since the blower cover abuts against the support base when the blower opening is closed, the blower cover is in close contact with the surface of the support as a flat surface, and has a remarkable shielding effect. DRAWINGS

1 is a front outward view of a refrigerator in accordance with an embodiment of the present invention.

2 is a side cross-sectional view showing a schematic structure of a refrigerator in accordance with an embodiment of the present invention. 3 is a front schematic view illustrating a supply air path of a refrigerator in accordance with an embodiment of the present invention.

Figure 4 is a side cross-sectional view showing the structure in the vicinity of a cooling chamber of a refrigerator in accordance with an embodiment of the present invention.

Figure 5 is an exploded perspective view showing a shielding device used in a refrigerator according to an embodiment of the present invention, wherein (A) and (B) are perspective views.

Figure 6 is a schematic diagram showing the results of air flow analysis around the axial flow fan under different conditions, where (A) the difference between the outlet side and the suction side is 12 Pa, and (B) the difference between the outlet side and the suction side 4Pa, (C) The difference between the bleed side and the suction side is 2Pa.

Fig. 7 is a front elevational view showing an example of a prior art refrigerator.

Figure 8 is a view showing an air volume control mechanism of another prior art refrigerator, wherein (A) is a cross-sectional view and (B) is a front view.

The reference numerals used in the figure are as follows:

1 refrigerator

2 insulation box

2a shell

2b liner

2c insulation material

3 cold storage room 5 upper freezer

6 lower freezer

7 vegetable room

8, 8a, 8b heat insulation door

9 insulated door

10 insulated door

11 insulated door

12 insulated door

13 cooling room

13a air supply

13b return air outlet

14 cold room supply air path

14a cold room supply air path

15 Freezer supply air path

16 vegetable room supply air path

17 blowout

18 blowout

19 blowout

20 Back to the wind

21 vegetable room return air path

22 return air outlet

23 return air outlet

24 return air outlet

25 refrigerator door damper

26 vegetable room damper

28 insulated partition wall

29 insulated partition wall

31 compressor

32 cooler

33 defrost heater

- 4 - Shishi

36 溺 redundant

36a Wind tunnel

37 fan

45 separator

46 separator

47 front cover

50 shielding device

51 blower cover

51b support hole

51i abutment

52 support base

52a frame

52b support frame

53 freezer temperature sensor

55 refrigerator temperature sensor

56 guide posts. detailed description

First Embodiment: Structure of a refrigerator

The configuration of a refrigerator according to an embodiment of the present invention will be described in detail below based on the drawings.

1 is a front outward view showing a schematic configuration of a refrigerator 1 according to an embodiment of the present invention. As shown in Fig. 1, the refrigerator 1 of the present embodiment has a heat insulating box 2 as a main body, and a storage chamber for storing food or the like is formed inside the heat insulating box 2. The interior of the storage compartment is divided into a plurality of storage compartments 3 to 7 according to the storage temperature and the use, wherein the uppermost compartment of the storage compartment is the refrigerating compartment 3, and the lower left side of the refrigerating compartment 3 is the ice making compartment 4 and the refrigerating compartment 3 The lower right side of the lower layer is the upper freezing compartment 5, the lower layer of the ice making compartment 4 and the upper freezing compartment 5 is the lower freezing compartment 6, and the lowermost layer of the storage compartment is the vegetable compartment 7. Further, the ice making compartment 4, the upper freezing compartment 5, and the lower freezing compartment 6 are storage compartments whose temperatures are in the freezing temperature range, and will be collectively referred to as an ice making compartment in the following description.

The front side of the heat insulating box 2 is open, and the heat insulating doors 8 to 12 which are openable and closable are provided in the opening corresponding to each of the storage chambers 3 to 7. The heat insulating doors 8a, 8b separately cover the front side of the refrigerating compartment 3, The upper left upper portion of the heat insulating door 8a and the right upper and lower portions of the heat insulating door 8b are rotatably supported by the heat insulating box 2. Further, the heat insulating doors 9 to 12 are integrally combined with the corresponding storage containers, and are supported by the heat insulating box 2 so as to be able to be pulled out in front of the refrigerator 1.

Fig. 2 is a side cross-sectional view showing a schematic structure of the refrigerator 1. As shown in FIG. 2, the heat insulating box 2 as the main body of the refrigerator 1 includes: a steel plate outer casing 2a opened at the front side, a synthetic resin inner liner 2b which is disposed in the outer casing 2a and is open at the front side, and the outer casing 2a and The foamed polyurethane heat insulating material 2c formed by filling and foaming is formed in the gap between the inner liners 2b. Further, each of the heat insulating doors 8 to 12 may have the same heat insulating structure as that of the heat insulating box 2.

The refrigerating compartment 3 is separated from the ice making compartments 4 to 6 located thereunder by an insulating partition wall 28. The ice making compartment 4 inside the ice making compartments 4 to 6 and the upper freezing compartment 5 are separated by a partition wall (not shown). Further, the ice making compartment 4 and the upper freezing compartment 5 communicate with the lower freezing compartment 6 provided below them, and cold air can flow therebetween. Further, the ice making compartments 4 to 6 and the vegetable compartment 7 are separated by a heat insulating partition wall 29.

On the rear side of the refrigerating compartment 3, a refrigerating compartment supply air passage 14 which is partitioned by a synthetic resin separator 45 and serves as a supply air passage for supplying cold air to the refrigerating compartment 3 is formed. An air outlet 17 for supplying a cold air into the cold chamber 3 is formed in the refrigerating compartment supply air passage 14. Further, a refrigerating compartment damper 25 is provided in the refrigerating compartment supply air passage 14. The refrigerating compartment damper 25 is an openable and closable damper driven by a motor or the like for controlling the flow rate of the cold air supplied to the refrigerating compartment 3, thereby keeping the inside of the refrigerating compartment 3 at an appropriate temperature.

The rear side of the ice making compartments 4 to 6 is formed with a freezer compartment supply air passage 15 for supplying cold air cooled by the cooler 32 to the ice making compartments 4 to 6. A cooling chamber 13 is formed on the rear side of the freezer compartment supply air passage 15, and a cooler 32 (evaporator) for cooling the circulating air in the refrigerator is disposed inside.

The cooler 32 is connected to a compressor 31, a radiator (not shown), and an expansion valve (capillary tube) (not shown) via a refrigerant pipe to constitute a vapor compression refrigeration cycle. Further, in the refrigerator 1 according to the present embodiment, isobutyl hydrazine (R600a) is used as the refrigerant of the refrigeration cycle.

Further, the refrigerator 1 includes a refrigerating compartment temperature sensor 55 for detecting the internal temperature of the refrigerating compartment 3, a freezing compartment temperature sensor 53 for detecting the internal temperature of the ice making compartments 4 to 6, and various other sensors (not shown).

Further, the refrigerator 1 includes a control device (not shown) that performs predetermined algorithm processing based on input values of the respective sensors to control various components such as the compressor 31, the blower 35, the shielding device 50, and the refrigerating chamber damper 25. .

FIG. 3 is a front schematic view showing a schematic configuration of a supply air passage of the refrigerator 1. As shown in FIG. 3, the refrigerating compartment supply air passage 14 conveys cold air to the uppermost portion in the central portion of the refrigerating compartment 3, and then cools the air. It descends from both sides and is supplied to the cold chamber 3. Thereby, cold air can be efficiently supplied to the entire interior of the refrigerating compartment 3.

The refrigerator 1 includes a return air path 20 that allows air to flow from the refrigerating chamber 3 back to the cooling chamber 13 (see Fig. 2). A lower portion of the refrigerating compartment 3 is formed with a return air port 22 which is an opening of the refrigerating compartment 3 to the return air passage 20. The air in the refrigerating compartment 3 flows to the return air passage 20 via the return air passage 22, and flows to the lower side of the cooler 32.

Further, in front of the return air passage 20, air flowing through the cooler 32 is supplied to the vegetable compartment supply air passage 16 of the vegetable compartment 7. The vegetable compartment supply air passage 16 is branched upward from the freezer compartment supply air passage 15, and extends through the inside of the heat insulating partition wall 28 (see FIG. 2) above the ice making compartments 4 to 6, and then becomes a slave system. The rear sides of the ice chambers 4 to 6 extend downward. Then, connect to the vegetable compartment 7 through the insulated partition wall 29 (see Figure 2). The vegetable compartment 7 is formed with an air outlet 19 which is an opening for blowing cold air from the vegetable compartment supply air passage 16 into the vegetable compartment 7.

The vegetable compartment supply air passage 16 is provided with a vegetable compartment damper 26 for controlling the flow of cold air supplied to the vegetable compartment 7. Thereby, the vegetable compartment 7 can be cooled independently of the cooling of the refrigerating compartment 3, so that the temperature of the vegetable compartment 7 can be appropriately controlled.

Further, the vegetable compartment supply air passage 16 may be configured to be branched from the side or the lower side of the freezer compartment supply air passage 15. Thereby, the vegetable compartment supply air passage 16 can be shortened, and the pressure loss can be reduced.

Further, the vegetable compartment supply air passage 16 can be connected to the return air passage 20 that returns the cold air from the refrigerating compartment 3. Thus, the vegetable compartment supply air passage 16 can be configured to be branched from the return air passage 20, and the cost can be reduced by omitting the vegetable compartment damper 26.

The vegetable compartment 7 is formed with a return air port 24, and the air in the vegetable compartment 7 flows from the return air outlet 24 to the lower portion of the cooling chamber 13 through the vegetable compartment return air passage 21 (refer to Fig. 2) and the return air outlet 13b (see Fig. 2).

Fig. 4 is a side cross-sectional view showing the structure in the vicinity of the cooling chamber 13 of the refrigerator 1. As shown in Fig. 4, the cooling chamber 13 is provided inside the heat insulating box 2 on the rear side of the freezing chamber supply air passage 15. The cooling chamber 13 and the freezing chamber supply air passage 15 or the ice making chambers 4 to 6 are separated by a synthetic resin separator 46. That is, the cooling chamber 13 is a space formed by the sandwich 2b and the separator 46.

The freezer compartment supply air passage 15 formed in front of the cooling chamber 13 is a space formed between the partition body 46 and the synthetic resin front cover 47 assembled in front thereof, and serves as a wind passage for cooling air cooled by the cooler 32. . The front cover 47 is formed with an air outlet 18 serving as an opening for blowing cold air into the ice making chambers 4 to 6. A return air opening 23 through which the air returns from the ice making chambers 4 to 6 to the cooling chamber 13 is formed on the lower back surface of the lower freezing compartment 6. Further, a return air port 13b is formed below the cooling chamber 13, and is connected to the air return port 23, and the return cold air from the storage chamber is sucked into the inside of the cooling chamber 13.

Further, a defrosting heater 33 is provided below the cooler 32, which serves as a defrosting means for melting and removing the frost attached to the cooler 32. The defrosting heater 33 is a resistance heating heater. Further, as the defrosting means, other defrosting methods such as shutdown defrosting or hot air defrosting without using an electric heater may be employed.

An air supply port 13a is formed in the partition 46 at the upper portion of the cooling chamber 13 as an opening connected to the refrigerating chambers 3 to 7. BP, the air supply port 13a is an opening through which the cooling air cooled by the cooler 32 flows, and connects the cooling chamber 13, the refrigerating compartment supply air passage 14, the freezing compartment supply air passage 15, and the vegetable compartment supply air passage 16 (see Fig. 3). The air supply port 13a is provided with a blower 35 for conveying cold air to the ice making compartments 4 to 6.

The blower 35 is an axial flow blower having a rotary fan 37 (propeller fan) and a fan case 36, and the fan case 36 is formed with a wind tunnel 36a having a substantially cylindrical opening. The fan casing 36 is attached to the air supply port 13a of the cooling chamber 13, and is a member that serves as a boundary between the suction side and the air outlet side of the blower 35.

Further, a fan 37 is provided coaxially with the wind tunnel 36a on the fan casing 36. Further, the wind-side end portion of the fan 37 is provided closer to the wind-side end portion of the wind tunnel 36a, that is, to the outside of the wind-side side end surface of the fan casing 36, that is, closer to the air outlet side or the freezer compartment. Supply the side of the wind path 15. Thereby, the flow resistance of the exhaust air flowing in the radial direction of the rotation of the fan 37 is reduced, and the cold air can be sent out with a small flow loss.

Further, outside the air supply port 13a of the cooling chamber 13, i.e., the air outlet side of the blower 35, a shielding device 50 is provided, and the shielding device 50 includes a blower cover 51 for closing the air blowing port 13a. The shielding device 50 is mounted such that its supporting base 52 is in close contact with, for example, the fan casing 36 of the blower 35.

The blower cover 51 is substantially in the shape of a cover. Thereby, the blower cover 51 does not come into contact with the fan 37 that protrudes toward the air outlet side from the fan casing 36, and can abut against the support base 52 outside the wind tunnel 36a, thereby closing the air supply port 13a.

5(A) and 5(B) are perspective views showing the structure of a blower 35 and a shielding device 50 of the refrigerator 1 according to an embodiment of the present invention, wherein Fig. 5(A) shows a state in which the blower cover 51 is closed, Fig. 5 (B) shows a state in which the blower cover 51 is opened.

The air outlet side end faces of the fan case 36 are fixed in close contact with the support base 52 of the shielding device 50. The support base 52 is a substantially flat portion having a cold air flowable opening at a substantially central portion. The member has a function of guiding the blower cover 51 and mechanically supporting the drive mechanism. On the main surface on the side of the ice making chambers 4 to 6 (see FIG. 4) of the support base 52, a guide post 56 is provided, and the blower cover 51 is reciprocally supported on the guide post in the direction of the rotation axis (Z direction) of the fan 37. 56 on. BP, a guide post 56 extending in the direction of the rotation axis (Z direction) of the fan 37 is slidably inserted into the support hole 51b of the blower cover 51. Thereby, the blower cover 51 can approach the blower 35 as shown in FIG. 5(A); or as shown in FIG. 5(B), away from the blower 35.

As shown in Fig. 5(A), if the blower cover 51 approaches the blower 35, the abutting portion 51i around the blower cover 51 abuts against the main surface of the support base 52, thereby closing the air flow path of the blower 35. That is, the blower port 13a (see Fig. 4) of the cooling chamber 13 (see Fig. 4) is closed by the blower cover 51, and a part of the air flow path is turned off. Specifically, by closing the blower cover 51, the flow path of the air passage 15 is supplied from the air supply port 13a to the freezer compartment.

In the present embodiment, the surface of the support base 52 is a flat surface, so that the peripheral portion of the blower cover 51, that is, the abutment portion 51i and the surface of the support base 52 can form a substantially gap-free close contact. Therefore, by thus shielding the shielding device 50, the air passage can be almost completely blocked to prevent air leakage.

On the other hand, as shown in FIG. 5(B), when the blower cover 51 is moved away from the blower 35, a gap is formed between the abutting portion 51i at the periphery of the blower cover 51 and the support base 52, that is, it is formed for The opening of the air flow. In other words, the blower cover 51 is opened and the air passage is in communication. Further, as indicated by an arrow V, the air blown by the blower 35 flows out from an opening formed between the abutting portion 51i of the blower cover 51 and the support base 52.

Thus, the blower cover 51 is moved away from the support base 52 attached to the blower 35, and cold air can be supplied to both the refrigerating compartment 3 and the ice making compartments 4 to 6. Thereby, the size of the air passage (air volume) can be uniformly adjusted. Specifically, when the general swinging damper is used to open the air passage, the damper is inclined with respect to the direction in which the cold airflow passes, and the circulation of the cold air may become uneven, and the air volume adjustment may be difficult. On the other hand, in the present embodiment, as described above, by separating the blower cover 51 from the support base 52, a gap can be formed therebetween, and cold air is supplied to the refrigerating chamber 3 or the like via the gap. Therefore, the blower cover 51 that is shielded from the wind path and opened does not hinder the flow of the cold air, and the air volume can be easily adjusted by adjusting the gap between the blower cover 51 and the support base 52.

Further, various methods can be employed for the mechanism and the driving method for opening and closing the blower cover 51. For example, the blower cover 51 can be opened and closed by a screw mechanism, a motor, a solenoid, or the like. Further, a member corresponding to the support base 52 of the shielding device 50 may be fixed to the front cover 47. The structure of the blower cover 51 and the fan case 36 is realized by the structure of (see Fig. 4).

Further, referring to Fig. 5 (A), an electric heater (heat generating body) may be provided on a driving mechanism of the blower cover 51 for driving the support base 52. Specifically, an electric heater is disposed inside or around the screw mechanism that drives the support base 52. Thereby, even if the moisture adhering between the driving mechanism and the blower cover 51 is frozen, it can be melted by the electrothermal heater, so that the operation of the driving mechanism due to freezing can be prevented from occurring.

Here, the air flow around the blower 35 will be described in more detail with reference to Figs. 6(A) to 6(C). 6(A) to 6(C) are schematic diagrams showing the analysis results of the air flow under different conditions around the axial flow fan as the blower 35, wherein Fig. 6(A) is the pressure on the outlet side and the suction side. The analysis result when the difference is 12 Pa, Fig. 6 (B) shows the analysis result when the pressure difference is 4 Pa, and Fig. 6 (C) shows the analysis result when the pressure difference is 2 Pa.

In Figs. 6(A) to (C), the symbol V is the wind speed vector distribution of the surface of the frame portion 52a of the support base 52 (see Fig. 6). Further, in the case where the support base 52 is not attached to the fan case 36, the symbol V corresponds to the wind speed vector distribution of the wind-side end surface of the fan case 36. Further, the symbol VI indicates the wind speed vector distribution on the surface S1 on the suction side (the right side of the paper surface), and the symbol V2 indicates the wind speed vector distribution on the surface S2 on the air outlet side (the left side of the paper surface). Each of the wind speed vectors V, VI, and V2 is expressed as: the direction of the arrows is the direction of each airflow, and the length of the arrows is proportional to the speed of each airflow. Further, in each of the figures, the horizontal line M drawn above and below the fan 37 is used to facilitate the calculation of the line used, and is not used to explain the analysis result, and the horizontal line can be ignored.

As shown in Fig. 6(C), when the pressure difference between the air outlet side and the suction side of the blower 35 is 2 Pa, the wind speed vector V on the air outlet side of the blower 35 is slightly inclined with respect to the vertical direction of the figure, but basic Towards the left side. Further, the wind speed vector V2 on the surface S2 on the air outlet side also protrudes to the left side. That is, it can be seen that, under the condition that the pressure difference is 2 Pa, the flow of the air on the air outlet side of the blower 35 is large in the direction of the rotational axis Z of the fan 37, and the speed in the direction of the rotational radius R is small. In other words, the air discharged from the blower 35 mainly flows toward the front of the blower 35.

However, as shown in Fig. 6(B), if the pressure difference between the air outlet side and the suction side of the blower 35 is 4 Pa, the wind speed vector V on the air outlet side of the blower 35 is slightly enlarged in the vertical direction of the figure, and the air is discharged. The wind speed vector V2 on the side surface S2 becomes shorter. BP, if the pressure difference becomes as large as 4 Pa, the speed of the air flow on the air outlet side of the blower 35 in the direction of the rotational radius R of the fan 37 becomes large.

Further, as shown in FIG. 6(A), if the pressure difference is further increased to 12 Pa, the air is supplied. The wind speed vector V on the air outlet side of the machine 35 is substantially oriented in the vertical direction of the figure. Further, the wind speed vector V2 on the surface S2 on the air outlet side becomes very short. BP can be seen that, under the condition that the pressure difference is 12 Pa, the speed of the air flow blown by the blower 35 in the direction of the rotation axis Z of the fan 37 becomes extremely small, and the speed in the direction of the radius of rotation R becomes large. In other words, the air blown by the blower 35 does not flow to the front of the blower 35 (i.e., in the Z direction), but flows in the direction of the radius of rotation 11.

Further, in any of the conditions of Figs. 6(A) to 6(C), the air flow on the air outlet side of the blower 35 forms a swirling flow centering on the rotating shaft of the fan 37.

The characteristics of the axial flow fan as the blower 35 have been described above. According to the refrigerator 1 of the present embodiment, in the refrigerator which forcibly circulates the cold air in the closed circuit, the pressure difference between the air outlet side and the suction side of the blower 35 is 10 ~12Pa or so. That is, as shown in Fig. 6(A), the cold air blown by the blower 35 is expanded toward the direction of the radius R of the fan 37 of the blower 35.

Therefore, the blower cover 51 according to the present embodiment moves away from the cooling chamber 13 while cooling the ice making chambers 4 to 6, and an opening for the flow of the cold air is formed between the blower cover 51 and the cooling chamber 13. Therefore, as described above, the air blown by the blower 35 having a large flow velocity in the direction of the radius of rotation R passes through the opening along the fan casing 36 and the partition 46, and flows into the freezer compartment supply passage with a very small flow resistance. 15 (and the cold room supply air duct 14).

At this time, as shown in Fig. 6(A), since the air flowing to the front of the blower 35 starts very little, the blower cover 51 that has been moved away from the cooling chamber 13 has a very small influence on the air passage resistance.

Further, as shown in Fig. 5(B), in order to prevent the pressure loss caused by the blower cover 51 from increasing, it is necessary to ensure the distance X between the main surface of the support base 52 and the end surface of the blower 35 of the blower cover 51 (i.e., to form air). The distance X) of the flow path opening has a specific length. Specifically, the distance X should be 30 mm or more, and more preferably 50 mm or more. If the distance X is shorter than 30 mm, the flow loss caused by the blower cover 51 is increased, and it is difficult to suppress the pressure loss to be small as compared with the case of using a damper or the like in the prior art.

On the other hand, if the distance X is ensured to be 50 mm or more, the pressure loss due to the increase of the blower cover 51 can be almost eliminated. This can be briefly explained with reference to Fig. 6 (A), and the wind-side surface S3 shown in the figure is at a position where the distance X (see Fig. 5 (B)) is equal to 50 mm. Further, the surface S2 is at a position where the distance X is 80 mm. As can be seen from the figure, as long as the opening is secured to the position of the surface S3, i.e., to a position where the distance X is 50 mm, the airflow is hardly hindered through the opening.

Second Embodiment: Working Process of Refrigerator Next, the operation of the refrigerator 1 having the above-described structure will be described with reference to Figs. 2 to 6 again.

First, the operation of cooling the refrigerating compartment 3 will be explained. As shown in Fig. 2, the compressor 31 is operated to open the refrigerating compartment damper 25, and the blower 35 is operated to cool the refrigerating compartment 3. That is, the air cooled by the cooler 32 is sequentially supplied to the refrigerating compartment 3 through the air supply port 13a (the blower 35) of the cooling chamber 13, the refrigerating compartment damper 25, the refrigerating compartment supply air passage 14, and the air outlet 17. Thereby, the food or the like stored in the refrigerating compartment 3 can be cooled and stored at an appropriate temperature.

At this time, referring to Fig. 4, the shielding device 50 is brought into an open state, and the cooling chamber 13 and the refrigerating chamber supply air passage 14a are brought into a communication state. BP, shielding device 50 As shown in Fig. 5 (B), the blower cover 51 and the support base 52 are separated, and the cooled air is supplied to the refrigerating chamber 3 from the gap therebetween.

Further, as shown in Fig. 3, the circulating cold air supplied into the refrigerating compartment 3 is returned from the return air passage 22 to the cooling chamber 13 via the return air passage 20. Therefore, the cooler 32 will cool it again.

Next, the operation of cooling the ice making chambers 4 to 6 will be explained. As shown in Fig. 2, the compressor 31 is operated, the blower 35 is operated, and the blower cover 51 is opened, whereby the ice making chambers 4 to 6 can be cooled. Specifically, the blower cover 51 is in a state of leaving the blower 35 as shown in Fig. 5(B). As a result, the air cooled by the cooler 32 is sent out through the blower 35 disposed at the air supply port 13a of the cooling chamber 13, and sequentially supplied to the ice making chambers 4 to 6 through the freezing chamber supply air passage 15 and the air outlet 18.

Therefore, it is possible to cool and store foods and the like stored in the ice making chambers 4 to 6 at an appropriate temperature. Further, the air in the ice making compartments 4 to 6 passes through the return air opening 23 formed on the rear side of the lower freezing compartment 6, and flows back to the cooling chamber 13 through the return air opening 13b of the cooling chamber 13.

Next, the supply of cold air to the vegetable compartment 7 will be explained. By opening the vegetable compartment damper 26, a part of the air sent to the freezer compartment supply air passage 15 by the blower 35 flows to the vegetable compartment supply air passage 16 as shown in Fig. 3, and is then blown from the air outlet 19 to the vegetable compartment 7. Thereby, the inside of the vegetable compartment 7 can be cooled. Further, the cold air circulating in the vegetable compartment 7 is returned from the return air outlet 24 shown in Fig. 2 to the cooling chamber 13 through the vegetable compartment return air passage 21 and the return air outlet 13b.

As described above, in the refrigerator 1, the cold air cooled by one cooler 32 can be efficiently supplied to the refrigerating chambers 3 to 7 independently with less pressure loss. Thereby, the refrigerating compartment 3 and the ice making compartments 4 to 6 can be appropriately cooled in accordance with the respective cooling loads.

Further, since the refrigerator 1 does not require a cooler dedicated to refrigeration, the refrigerator compartment 3 can be enlarged. Further, the cooling temperature of the cooler 32 (the evaporation temperature of the refrigerant) can be adjusted in accordance with the target cooling temperature of the storage chamber to which the cold air is to be supplied, whereby the efficiency of the refrigeration cycle can be further improved. Next, the operation performed at the time of the defrosting operation will be described with reference to Figs. 2, 4 and 5. If the cooling operation is continuously performed, the air-side heat transfer surface of the cooler 32 adheres to the frost, hinders heat transfer, and blocks the air flow path. Therefore, the frost is judged from the decrease in the evaporation temperature of the refrigerant or the like, or after the frosting is judged by the defrosting timer or the like, the defrosting cooling operation or the defrosting operation is started to remove the frost attached to the cooler 32.

First, a defrosting cooling operation for cooling the refrigerating compartment 3 by the latent heat of the frost attached to the cooler 32 will be explained. When the defrosting cooling operation is performed, the compressor 31 is stopped, and the blower cover 51 is opened as shown in Fig. 5 (B). Thereafter, the refrigerating compartment damper 25 is opened to operate the blower 35.

Thereby, air can be circulated between the refrigerating compartment 3 and the cooling chamber 13, and the circulating air is used to melt the frost adhering to the cooler 32. BP can perform defrosting without heating by the defrosting heater 33. At the same time, instead of operating the compressor 31, the refrigerating compartment 3 is cooled by the heat of melting of the frost.

Namely, it is possible to reduce the heater input for defrosting and the compressor input for cooling, reduce the power consumption of the refrigerator 1, and comprehensively improve the cooling efficiency. Further, since the cold air having a high humidity due to the defrosting can be supplied to the refrigerating compartment 3, it is possible to prevent the food or the like stored therein from being dried and to improve the fresh-keeping effect. Further, by providing a supply air passage for supplying cold air to the vegetable compartment 7 without passing through the freezer compartment supply air passage 15, it is possible to perform cooling and moisture supply by the defrosting latent heat even for the vegetable compartment 7.

Here, the aforementioned defrosting cooling operation is performed under the condition that it is judged that the cooler 32 is frosted and the temperature of the refrigerating compartment 3 is higher than a predetermined threshold. Even if it is detected that the cooler 32 is frosted, when the temperature of the refrigerating compartment 3 is lower than a predetermined threshold, it is not necessary to perform cooling of the refrigerating compartment 3, so that the defrosting cooling operation can be omitted, and the defrosting heater 33 can be used for conventional defrosting. operating.

A conventional defrosting operation will be described below. In the conventional defrosting operation, the compressor 31 is stopped, and the defrosting heater 33 is energized to melt the frost adhering to the cooler 32. At this time, the blower port 13a is closed by the blower cover 51, and the refrigerating compartment damper 25 is closed. BP, the shielding device 50 becomes the shielding state shown in Fig. 5 (A). Thereby, it is possible to prevent the air in the cooling chamber 13 heated by the defrosting heater 33 from flowing into the cold chamber supply air passage 14 or the like. As a result, the cooling efficiency of the refrigerator 1 can be improved.

Further, when the defrosting of the cooler 32 is completed, the energization of the defrosting heater 33 is stopped, and the compressor 31 is started to start the cooling by the refrigeration circuit. Moreover, after detecting the cooler 32 and cooling After the chamber 13 is cooled to a predetermined temperature or a timer or the like has elapsed for a predetermined period of time, the blower cover 51 and the refrigerating chamber damper 25 are opened, and the blower 35 is started to operate. Thereby, the influence of the defrosting tropics can be suppressed as small as possible, and the cooling operation can be started again.

Next, the operation of forming the air curtain will be explained with reference to Fig. 2 . If it is detected that the heat insulating door 8 is in the open state, the refrigerating compartment damper 25 is opened, and the blower 35 is operated. Thereby, cold air is blown downward from the air outlet 17 formed in the front portion of the upper surface of the refrigerator compartment 3, and a wind curtain is formed in the front opening of the refrigerator compartment 3.

Further, a flap (not shown) whose opening degree is adjustable may be provided at the air outlet 17 at the front of the upper surface of the refrigerating compartment 3. By providing the flap and adjusting its angle (opening), a suitable air curtain for preventing leakage of cold air from the inside to the outside of the refrigerating compartment 3 can be formed. Further, the blower 35 can be continued to operate for a predetermined period of time after the heat insulating door 8 is closed, and the flap can also be swung. Thereby, it is possible to effectively cool the inside of the refrigerating compartment 3 which is warmed by opening the heat insulating door 8, in particular, the housing wall box 57 inside the heat insulating door 8.

As described above, the refrigerator 1 according to the present embodiment can close the air supply port 13a of the cooling chamber 13 by the blower cover 51 during the defrosting process, thereby preventing the hot air flow during defrosting from entering the storage chamber.

Further, the blower cover 51 according to the present embodiment is attached to the outside of the air supply port 13a of the cooling chamber 13, i.e., the air outlet side of the blower 35, so that it can be used for other types of ice bins having different air passage shapes. At this time, the blower cover 51 and the blower 35 can be formed as one structural member that is integrally assembled. Thereby, the defrosting hot air leakage can be prevented regardless of the air passage structure, so that the degree of freedom in designing the cooling air passage can be increased, and the air passage design can be easily performed. Therefore, the development cost and production cost of the cooling air passage and the damper can be reduced.

Claims

Rights request

A refrigerator comprising:

Storage room

a cooling chamber is formed with a blowing opening portion and a return air opening portion respectively connected to the storage chamber; a cooler disposed inside the cooling chamber to cool air flowing in from the return air opening portion;

a blower disposed at the air supply opening portion;

a defrosting mechanism that defrosts the cooling chamber;

a shielding device that closes the air blowing opening from an outer side of the cooling chamber;

The refrigerator is characterized in that

The shielding device has a blower cover that closes the air supply opening portion, and a support base disposed between the air blower and the blower cover.

The blower cover abuts against the support base when the air supply opening is closed.

2. Apparatus according to claim 1 wherein:

A guide post slidably penetrating the blower cover is disposed on the support base.

3. Apparatus according to claim 1 or 2, characterized in that

A heating element is provided on the support base or at a peripheral portion of the support base.

The refrigerator according to any one of claims 1 to 3, characterized in that

The blower cover is brought into a communication state by moving in a direction away from the blower.