CN110094924B

CN110094924B - Refrigerator with a door

Info

Publication number: CN110094924B
Application number: CN201811032562.9A
Authority: CN
Inventors: 板仓大; 冈田福太郎; 河井良二; 冈留慎一郎; 额贺晴树; 盐野谦治; 服部圭介
Original assignee: Hitachi Global Life Solutions Inc
Current assignee: Hitachi Global Life Solutions Inc
Priority date: 2018-01-31
Filing date: 2018-09-05
Publication date: 2021-09-17
Anticipated expiration: 2038-09-05
Also published as: CN110094924A

Abstract

The invention provides a refrigerator capable of efficiently defrosting a structure on the side of a cooler for cold storage. The refrigerator comprises a heat insulation box body forming a refrigerating temperature zone chamber and a freezing temperature zone chamber, a compressor, a refrigerating evaporator for cooling the refrigerating temperature zone chamber, a freezing evaporator for cooling the freezing temperature zone chamber, a first air blower for enabling the refrigerating evaporator to exchange heat with air in the refrigerating temperature zone chamber, and a second air blower for enabling the freezing evaporator to exchange heat with air in the freezing temperature zone chamber, wherein an air path passing through a pipe part of the refrigerating evaporator is formed on the upstream side of an air path passing through a fin part of the refrigerating evaporator in the vertical direction.

Description

Refrigerator with a door

Technical Field

The present invention relates to a refrigerator.

Background

There is a refrigerator provided with a cooler for cold storage for cooling a cold storage temperature zone chamber and a cooler for freezing for cooling a freezing temperature zone chamber. Here, as for defrosting of the cooler for cold storage, there is also known a defrosting method in which a fan for cold storage is driven during a freezing operation, that is, in a state where no refrigerant flows into the cooler for cold storage.

For example, patent document 1 describes a refrigerator in which a gas-liquid separator (accumulator) is provided on a side of a cooler for cold storage, and the end of defrosting is detected by a sensor provided in the gas-liquid separator.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open No. 2010-230251

Disclosure of Invention

Problems to be solved by the invention

The refrigerator described in patent document 1 is provided with a wind shielding portion that makes it difficult for air in the refrigerating region to flow toward the gas-liquid separator and makes it easy for the air to flow toward the cooler for refrigeration. Therefore, in the case of defrosting the cooler for cold storage by driving the fan for cold storage, although defrosting of the cooler body for cold storage (fin portion) is easy, defrosting of the gas-liquid separator and the heat transfer pipe located on the side of the cooler for cold storage is difficult because the return air from the cold storage temperature zone chamber hardly flows, and thus defrosting becomes difficult. In order to reliably defrost the gas-liquid separator and the duct portion, it is necessary to extend the driving time of the refrigerating fan, and energy saving performance is reduced.

The present invention has been made in view of the above problems, and an object thereof is to provide a refrigerator capable of efficiently defrosting a structure on a side of a cooler for cold storage.

Means for solving

To solve the above problem, for example, the structure described in the claims is adopted. The present application includes a plurality of solutions to the above-described problem, and an example thereof is a refrigerator including a heat insulating box body forming a refrigerating temperature zone chamber and a freezing temperature zone chamber, a compressor, a refrigerating evaporator for cooling the refrigerating temperature zone chamber, a freezing evaporator for cooling the freezing temperature zone chamber, a first blower for exchanging heat between the refrigerating evaporator and air in the refrigerating temperature zone chamber, and a second blower for exchanging heat between the freezing evaporator and air in the freezing temperature zone chamber.

The effects of the invention are as follows.

According to the present invention, it is possible to provide a refrigerator capable of efficiently defrosting a structure on the side of a cooler for cold storage.

Drawings

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

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

Fig. 3 is a sectional view B-B of fig. 1.

Fig. 4 is a structural view of a freezing cycle of the refrigerator of the embodiment.

Fig. 5 is a configuration of a heat dissipation mechanism of the refrigerator of the embodiment.

Fig. 6 is a structural view of an evaporator of the refrigerator of the embodiment.

Fig. 7 is a perspective view of the blower for the freezing compartment of the embodiment.

Fig. 8 is a perspective view of a blower for a refrigerator according to an embodiment.

Fig. 9 (a) is a cross-sectional view showing a comparative example in a case where one propeller fan is vertically mounted, (b) is a cross-sectional view showing a comparative example in a case where one propeller fan is horizontally mounted, and (c) is a cross-sectional view showing a comparative example in a case where one small-diameter propeller fan is horizontally mounted.

Fig. 10 is a graph showing a relationship between the fan aerodynamic characteristics and the resistance curve of fig. 9 (b) and 9 (c).

Fig. 11 is a graph of the relationship between the fan aerodynamic characteristics and the resistance curve of fig. 8 (a) and 10.

Fig. 12 is a sectional view of a case where the turbofan according to the embodiment is vertically mounted.

Fig. 13 is a cross-sectional view C-C of fig. 12.

Fig. 14 is a diagram showing an example of the operation mode.

Fig. 15 is an enlarged view of the refrigerating compartment of fig. 3.

Fig. 16 is a diagram showing a relationship between a shelf and a blowing path of the refrigerating compartment according to the embodiment.

Fig. 17 is a view showing a mounting manner of the blower to the casing.

Fig. 18 is a diagram showing the configuration of the first locking portion and the second locking portion.

Fig. 19 is a sectional view a-a of fig. 17.

Description of the symbols

1-refrigerator, 2-refrigerating chamber, 3-ice making chamber, 4-upper freezing chamber, 5-lower freezing chamber, 6-vegetable chamber, 7-freezing chamber (3, 4, 5), 10-cabinet, 10 a-outer cabinet, 10 b-inner cabinet, 11-vacuum heat insulating material, 12a, 12b, 12 c-heat insulating partition wall, 13-door pocket, 14a, 14b, 14c, 14 b-shelf, 15-ice fresh chamber, 16a, 16 b-evaporator chamber, 17-outer casing, 17 a-lower surface of outer casing, 17 b-inlet of outer casing, 17 c-tongue of outer casing, 17 d-first locking part, 17 e-second locking part, 18a, 18 b-output air passage, 19a, 19 b-output port, 20a, 20b, 20 c-return port, 21-opening part, 21 a-turning wall (resistance adding mechanism), 22-return, 23a, 23 b-air passage, 24a, 24b heater, 25a, 25b drain pipe, 26 evaporating pan, 27 cover, 28 temperature/humidity sensor, 29 control board, 30 depth dimension of air supply path around

blower

112a, 31 depth dimension of

evaporator

105a, 32 dimension of output air path perpendicular to air flow direction, 33 communication flow path, 40 separator, 41 upper surface of separator, 50 wind direction plate, 52 heat insulating material, 53 cover, 60 minimum width of communication flow path 33 from opening 21 to evaporator chamber 16a, minimum width between blades of blower 112a, 62 first air path, 63 second air path, 71 rotating body, 72 support, 73 rubber seat, 100 compressor, 101 out-of-box radiator, 102 side radiating pipe, 103 front radiating pipe, 104a, 104b capillary, 105a, 105b, and, 105 b-evaporator, 106a, 106 b-gas-liquid separator, 107-three-way valve, 108-check valve, 109-dryer, 110-refrigerant merging portion, 111-refrigerant pipe, 112a, 112 b-blower, 113-blower, 114-machine room, 115-fin, 116-heat transfer tube.

Detailed Description

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

[ examples ] A method for producing a compound

An embodiment of a refrigerator of the present invention will be explained with reference to fig. 1 to 16.

Fig. 1 is a front view of a refrigerator of the embodiment. As shown in fig. 1, a refrigerator 1 according to the present embodiment includes a refrigerating compartment 2, an ice making compartment 3, an upper freezing compartment 4, a lower freezing compartment 5, and a vegetable compartment 6, which are arranged side by side in this order from above. Hereinafter, ice making compartment 3, upper-stage freezing compartment 4, and lower-stage freezing compartment 5 are collectively referred to as freezing compartment 7. Refrigerating room 2 includes a rotary refrigerating room door 2a and a door 2b that are split into two halves, and ice making room 3, upper freezing room 4, lower freezing room 5, and vegetable room 6 include a drawer-type door 3a, a door 4a, a door 5a, and a door 6a, respectively. The height H1 of the refrigerating compartment 2 is greater than the height H2 of the freezing compartment 7 (H1 > H2).

Freezing chamber 7 is a storage chamber having a freezing temperature zone (less than 0 ℃) in the interior of the refrigerator, for example, an average temperature of about-18 ℃, refrigerating chamber 2 and vegetable chamber 6 are a refrigerating temperature zone (0 ℃ or higher), for example, refrigerating chamber 2 is a storage chamber having an average temperature of about 4 ℃, and vegetable chamber 6 is a storage chamber having an average temperature of about 7 ℃. By disposing freezer compartment 7 of the storage compartments between refrigerating compartment 2 and vegetable compartment 6, the area of freezer compartment 7 having the lowest temperature in contact with the outside air can be minimized, and therefore the amount of heat intrusion from the outside air into refrigerator 1 is reduced, and the energy saving performance of refrigerator 1 is improved.

Fig. 2 is a sectional view a-a of fig. 1, and fig. 3 is a sectional view B-B of fig. 1. As shown in the drawing, the refrigerator 1 is partitioned between the outside and inside by a cabinet 10 formed by filling a foam heat insulating material (e.g., foam urethane) between an outer cabinet 10a and an inner cabinet 10 b. A plurality of vacuum insulation materials 11 (dotted lines in fig. 3) are installed between the outer case 10a and the inner case 10b in the case 10 in addition to the foam insulation material. Here, the vacuum insulation material 11 is configured by wrapping a core material such as glass wool or polyurethane with a wrapping material. Since the envelope includes a metal layer (e.g., aluminum) in order to secure the gas barrier property, the outer circumferential side of the vacuum insulation material 11 is easily conducted with heat by the heat conduction of the envelope.

The refrigerating chamber 2 and the upper-stage freezing chamber 4 and the ice-making chamber 3 are partitioned by a heat-insulating partition wall 12a, and similarly, the lower-stage freezing chamber 5 and the vegetable chamber 6 are partitioned by a heat-insulating partition wall 12 b. In order to prevent air inside and outside the refrigerator from flowing through the gaps between

doors

3a, 4a, and 5a, heat insulating partition walls 12c are provided on the front surface sides of the storage compartments of ice making compartment 3, upper-stage freezing compartment 4, and lower-stage freezing compartment 5. A plurality of door pockets 13 and a plurality of

shelves

14a, 14b, 14c, 14d are provided inside the

doors

2a, 2b of the refrigerating chamber 2 to divide into a plurality of storage spaces. The

shelf plates

14a, 14b, 14c, and 14d are supported by support portions (not shown) provided on the inner box 10b on both side surfaces. Since the support portions are provided at different heights of the

shelf plates

14a, 14b, and 14c, the installation heights of the

shelf plates

14a, 14b, and 14c can be adjusted according to the storage items.

Freezing room 7 and vegetable room 6 include an ice making room container (not shown), an upper freezing room container 4b, a lower freezing room container 5b, and a vegetable room container 6b, which are respectively drawn out integrally with

doors

3a, 4a, 5a, and 6 a.

A freezing compartment 15 whose temperature is set to be lower than the temperature range of the refrigerating compartment 2 is provided above the heat insulating partition wall 12 a. The freezing chamber 15 can be switched between a mode of about 0 to 3 ℃ in a refrigerating temperature range and a mode of about-3 to 0 ℃ in a freezing temperature range, for example, by controlling the evaporator 105a and the blower 112a and a heater (not shown) provided in the heat insulating partition wall 12a, for example.

The evaporator 105a is a cross fin tube heat exchanger for the freezing chamber 7, and is provided in an evaporator chamber 16a provided on the back side of the refrigerating chamber 2. The air that has exchanged heat with evaporator 105a and has become low temperature is blown by blower 112a provided at a position higher than evaporator 105a to refrigerating compartment 2 through casing 17, output air duct 18a, and output port 19a opened upward, thereby cooling the inside of refrigerating compartment 2. The air supplied to the refrigerating compartment 2 is returned to the evaporator 105a from the return port 20a located below the evaporator chamber 16 a.

The housing 17 has an opening 21 at a lower portion thereof. This suppresses the accumulation of dew condensation water flowing through output air duct 18a, thereby preventing malfunction of blower 112 a.

By operating the blower 112a without flowing the refrigerant in the evaporator 105a, the frost grown on the air side surface of the evaporator 105a can be melted without using a heat source such as a heater. In addition, since the air blown into refrigerating chamber 2 during the defrosting operation of evaporator 105a is about 0 ℃, refrigerating chamber 2 can be cooled while defrosting. Therefore, the embodiment of the present embodiment has the following configuration: since the refrigerator has lower power consumption than defrosting using a heat source such as a heater and can cool the refrigerating chamber 2 even during defrosting operation, the energy saving performance of the refrigerator 1 is not easily impaired even when defrosting operation is frequently performed.

A heater 24a is provided on the surface of the trough 23a located below the evaporator 105 a. By energizing the heater 24a, even if the water accumulated in the trough 23a freezes, the ice can be melted and drained. The melted water produced in the flow groove 23a is discharged to the evaporation pan 26 provided in the upper portion of the compressor 100 through the drain pipe 25 a.

The evaporator 105b is a cross fin tube heat exchanger for the freezing chamber 7, and is provided in an evaporator chamber 16b provided on the back side of the freezing chamber 7. Air having a low temperature resulting from heat exchange with evaporator 105b is blown into freezing chamber 7 by blower 112b provided above evaporator 105b through output air duct 18b and output port 19b, thereby cooling the inside of freezing chamber 7. The air after being supplied to the freezing chamber 7 passes through the freezing chamber return port 20b located below the evaporator chamber 105b and returns to the evaporator 105 b.

In the refrigerator 1 of the present embodiment, the vegetable compartment 6 is also cooled by directly blowing air that has become low temperature in the evaporator 105 b. The air in the evaporator chamber 16b that has been cooled in the evaporator 105b is blown into the vegetable compartment 6 by the blower 112b through a vegetable compartment air passage (not shown) and a vegetable compartment damper (not shown), thereby cooling the inside of the vegetable compartment 6. When the vegetable compartment 6 is at a low temperature, cooling of the vegetable compartment 6 is suppressed by closing the vegetable compartment damper. The air blown into vegetable compartment 6 is returned to evaporator compartment 16b through return duct 22 from return port 20c provided in front of the lower portion of heat-insulating partition wall 12 b. Here, a communication port (not shown) constituting a part of the vegetable compartment air passage is formed in the heat insulating partition wall 12b, and air having a low temperature in the evaporator 105b is supplied into the vegetable compartment 6 through the communication port.

A heater 24b is provided below the evaporator 105 b. By energizing the heater 24b, frost growing on the air-side surface of the evaporator 105b can be melted, and therefore deterioration of the cooling performance of the heat exchanger 105 can be suppressed. The melt water generated during defrosting falls into a trough 23b provided in the lower portion of the evaporator chamber 16b, and is discharged to an evaporation pan 26 provided in the machine chamber 114 above the compressor 100 via a drain pipe 25 b.

A temperature/humidity sensor 28 for detecting the temperature and humidity of the air outside the refrigerator is provided inside a cover 27 provided on the upper surface of the refrigerator 1. A control board 29 is disposed on the upper rear surface side of the refrigerator 1, and the freezing cycle and the blower system are controlled by a control unit stored in the control board 29.

Fig. 4 is a structural view of a freezing cycle of the refrigerator of the embodiment. The refrigerator 1 of the present embodiment includes a compressor 100 for compressing a refrigerant, an outdoor heat radiator 101 and a side heat radiation pipe 102 as heat radiation means, a front heat radiation pipe 103,

capillaries

104a and 104b for decompressing the refrigerant,

evaporators

105a and 105b as heat absorption means, gas-

liquid separators

106a and 106b for preventing a liquid refrigerant from flowing into the compressor 100, a three-way valve 107 for controlling a refrigerant flow path, a check valve 108 for preventing a reverse flow of the refrigerant, a drier 109 for removing moisture in a refrigeration cycle, and a refrigerant merging portion 110 for connecting the refrigerant flow paths, and the above components are connected by a refrigerant pipe 111 to circulate the refrigerant, thereby constituting the refrigeration cycle. Here, the evaporator 105a causes air to flow by the blower fan 112a, and the evaporator 105b causes air to flow by the blower fan 112b, thereby promoting cooling of the refrigerating chamber 2 and the freezing chamber 7. Similarly, the outside-box heat sink 101 promotes heat dissipation of the refrigerator 1 by flowing air with the blower 113.

The refrigerant output from the compressor 100 flows in order to the out-tank radiator 101, the side heat radiation pipe 102, the front heat radiation pipe 103, and the dryer 109, and reaches the three-way valve 107. The three-way valve 107 includes an outlet 107a and an outlet 107b, and the refrigerant flowing into the three-way valve 107 flows to either the outlet 107a or the outlet 107 b.

In the refrigeration mode in which the refrigerant flows toward the outflow port 107a, the refrigerant flows in the capillary tube 104a, the evaporator 105a, the gas-liquid separator 106a, and the refrigerant merging portion 110 in this order, and then returns to the compressor 100. The refrigerant that has become low-pressure and low-temperature in capillary tube 104a flows through evaporator 105a, and evaporator 105a exchanges heat with the air in refrigerating compartment 2, thereby cooling the contents in refrigerating compartment 2.

In the refrigeration mode in which the refrigerant flows toward the outflow port 107b, the refrigerant flows in the capillary tube 104b, the evaporator 105b, the gas-liquid separator 106b, the check valve 108, and the refrigerant merging portion 110 in this order, and then returns to the compressor 100. Here, the check valve 108 is disposed so as not to allow the refrigerant to flow from the refrigerant merging portion 110 toward the gas-liquid separator 106 b. The refrigerant that has become low-pressure and low-temperature in the capillary tube 104b flows through the evaporator 105b, and the evaporator 105b exchanges heat with the air in the freezing chamber, thereby cooling the contents in the freezing chamber 7.

Fig. 5 is a configuration of a heat dissipation mechanism of the refrigerator of the embodiment. The outdoor radiator 101 (not shown) is a fin-tube heat exchanger disposed in the machine room 114, the side-surface radiator pipe 102 is a radiator pipe disposed along the side wall surface of the refrigerator 1, and the front-surface radiator pipe 103 is a radiator pipe disposed inside the front edge of the heat-insulating

partition walls

12a, 12b, 12c (see fig. 2) of the refrigerator 1. The side heat radiation pipe 102 is embedded in the refrigerator 1 on the side of the outer box 10a in the cabinet 10. The front heat radiation pipe 103 is buried in the front side of the refrigerator 1 where the heat insulating

partition walls

12a, 12b, and 12c (see fig. 2) dividing the storage compartments are located. The front heat dissipation pipe 103 not only dissipates heat, but also prevents condensation on the

heat insulating partitions

12a, 12b, and 12 c.

Fig. 6 is a configuration diagram of an evaporator of a refrigerator according to an embodiment, fig. 6 (a) shows a configuration diagram of a refrigerating evaporator, and fig. 6 (b) shows a configuration diagram of a freezing evaporator. As shown in fig. 6, the

evaporators

105a and 105b are cross fin tube heat exchangers, and are configured such that a heat transfer tube 116 bent multiple times penetrates a plurality of aluminum fins 115. In the present embodiment, the average stacking interval Pf1 of the fins of the evaporator 105a and the average stacking interval Pf2 of the fins of the evaporator 105b are in a relationship of Pf1 ≦ Pf2, the height H3 of the evaporator 105a and the height H4 of the evaporator 105b are in a relationship of H3 ≦ H4, and the width W1 of the evaporator 105a and the height W2 of the evaporator 105b are in a relationship of W1 ≦ W2. Accordingly, the evaporator 105b can suppress the flow of air from being blocked by frost growth while securing a heat transfer area, and the energy saving performance of the refrigerator 1 can be improved by reducing the number of times the heater 24b is energized. On the other hand, evaporator 105a can secure a heat transfer area and be miniaturized, and therefore, the internal volume of refrigerating room 2 can be increased without impairing energy saving performance.

In the present embodiment, Pf1 is set to 3mm, and Pf2 is set to 5 mm. By setting the size as above, even when frost grown on the evaporator 105a and the evaporator 105b melts, water can be reliably drained. Even in the case other than the dimensions used in the present embodiment, the same effect can be obtained if the relationship Pf1 ≦ Pf2 is established.

Fig. 7 is a perspective view of the blower for the freezing compartment of the embodiment. In the embodiment of the blower 112b for the freezing chamber 7 of the present embodiment, a propeller fan is used. In the present embodiment, the propeller fan has three blades, and the diameter of the blade is set to 110mm for about 1100-1600 min^-1Is operated at a rotational speed of (1). By operating the blower 112b, air is blown in the axial flow direction from the suction side to the discharge side of the fan.

As shown in fig. 2, the distance in the vertical direction of freezing room 7 is shorter than that of refrigerating room 2 (H1 > H2), and the distance in the vertical direction of evaporator 105b of freezing room 7 is longer than that of evaporator 105a of refrigerating room 2 (H4 > H3), so the path from the evaporator to the outlet is shorter. Therefore, the air output from the fan is output toward the front side of the freezing chamber 7. In such a front-face-blowing type air blowing path, by using a propeller fan that is mounted as a fan and that causes the same direction of suction and blowing, the arrangement of output air duct 18b and output port 19b can be simplified, and the air volume can be increased by reducing the ventilation resistance of freezing room 7.

In addition, in the freezing chamber 7 which is always in the subzero temperature zone and is difficult to defrost, a method such as a propeller fan in which the inter-blade pitch is wide is used, so that malfunction of the refrigerator 1 due to frost growth around the blower 112b is not easily caused.

Fig. 8 is a perspective view of a blower for a refrigerator according to an embodiment. In the embodiment of the blower fan 112a for the refrigerating compartment 2 of the present embodiment, a turbofan is used. As shown in the drawing, when the turbo fan is operated, air is sucked in from the axial direction of the turbo fan, and is sent to the outer peripheral side by centrifugal force, and is blown from the outer peripheral side along the entire circumference. Further, since the turbofan is a high static pressure type blower, it has a characteristic that the air volume is easily increased at a high static pressure (a large ventilation resistance) as compared with the propeller fan.

The reason why the turbofan is used will be described in detail below with reference to fig. 9 to 12.

Fig. 9 (a) is a cross-sectional view showing a comparative example in the case where one propeller fan is vertically mounted, fig. 9 (b) is a cross-sectional view showing a comparative example in the case where one propeller fan is horizontally mounted, and fig. 9 (c) is a cross-sectional view showing a comparative example in the case where one small-diameter propeller fan is horizontally mounted.

As shown in fig. 9 (a) to (c), a propeller fan is generally used as a blower for a refrigerating chamber.

As shown in fig. 9 (a), in the system in which the propeller fan serving as the blower 112a is disposed substantially vertically, a space for turning the direction of the flow is required on the front surface side and the rear surface side of the propeller fan. Therefore, depth 30 of the air passage around blower 112a is larger than depth 31 of evaporator 105a, and the internal volume of refrigerating compartment 2 is easily reduced.

As shown in fig. 9 (b), in the system in which the propeller fan as the blower 112a is disposed substantially horizontally, since there is no obstacle in the flow direction, the operation can be performed without impairing the blowing efficiency, but the depth dimension 30 of the blowing path around the blower 112a needs to be equivalent to the diameter of the blower 112 a. Therefore, depth 30 of the air passage around blower 112a is larger than depth 31 of evaporator 105a, and the internal volume of refrigerating compartment 2 is easily reduced.

As shown in fig. 9 (c), when the diameter D of the propeller fan serving as the blower 112a is reduced, the reduction of the internal volume can be suppressed, but the air volume is reduced, and the energy saving performance is degraded. Therefore, in the embodiment (c) of fig. 9, when a plurality of (for example, two) propeller fans as the fans 112a are arranged in parallel and substantially horizontally in the left-right direction of the refrigerator 1, the depth 30 of the air passage around the fan 112a can be made close to the depth 31 of the evaporator 105a, and a sufficient air volume can be ensured. However, since the fans 112a are arranged in parallel, when frost grows on the surface of the evaporator 105a and the air flow resistance increases, the air volume tends to decrease, and the energy saving performance may decrease. The reason will be described with reference to fig. 10.

Fig. 10 is a graph showing a relationship between the fan aerodynamic characteristics and the resistance curve of fig. 9 (b) and 9 (c). The solid line shows the mode (b) of fig. 9, the broken line shows a case where one propeller fan is arranged in the mode (c) of fig. 9, and the chain line shows a case where two propeller fans are arranged in parallel in the mode (c) of fig. 9. Here, for easy understanding of the characteristics, the rotation speeds of the fans are the same, and the respective operating points are indicated by black dots.

As shown in fig. 10 (a), in the normal operation in which the evaporator is not frosted, the resistance curve draws a gentle curve as shown in the drawing because the conditions of low static pressure and high air volume are satisfied. When the fan diameter is reduced (broken line) as shown in fig. 9 c, the air volume and the static pressure are reduced as compared with the mode (solid line) of fig. 9 b. In the embodiment of fig. 9 c, if two propeller fans (one-dot chain line) are provided, the air volume of static pressure 0 is 2 times larger than that of the case where one propeller fan is provided. Therefore, the system (two propeller fans) of fig. 9 (b) and the system (c) of fig. 9 can be operated with the same air volume.

As shown in fig. 10 (b), when frost grows on the surface of the evaporator, the resistance curve draws a steep curve as shown in the drawing because the conditions of high static pressure and low air volume are satisfied. Therefore, compared to the system of fig. 9 (b), the amount of air flow is reduced in the system of fig. 9 (c) (two propeller fans), and the energy saving performance of the refrigerator 1 is reduced.

The conventional example in which the propeller fan is mounted as described above has a problem in that the internal volume of the refrigerating compartment 2 is increased while energy saving performance is ensured, and the amount of air flow is easily reduced under the high-static-pressure low-air-flow condition even when the diameter and the number of the propeller fans are studied.

Fig. 11 is a graph showing a relationship between aerodynamic characteristics and resistance curves of a propeller fan and a turbofan having the same blade diameter and the same rotational speed. As shown in fig. 11 (a), during normal operation in which the evaporator 105a is not frosted, the same air volume can be ensured in the case where the turbo fan is attached and in the case where the propeller fan is attached. As shown in fig. 11 (b), when frost grows on the surface of the evaporator 105a, the air volume can be increased by installing the turbofan as in the present embodiment, as compared with the case where the propeller fan is installed. In the present embodiment, as described above, since the blower 112a is operated even during defrosting of the evaporator 105a, the efficiency of the defrosting operation is improved, and thus the energy saving performance of the refrigerator 1 can be improved.

As shown in the present embodiment, as a fan having a characteristic of blowing out a flow sucked in an axial direction in a radial direction, there is a sirocco fan other than the turbo fan used in the present embodiment. In general, the number of blades of the turbofan in the above-described method (centrifugal fan) is the smallest. The use of the turbofan having the smallest number of blades prevents clogging of the air flow due to frost growth between the blades and operation failure due to interference between the frost growth portion of the air duct and the blades.

As described above, according to the present embodiment, the propeller fan is selected for the fan 112b of the freezing compartment 7 and the turbo fan is selected for the fan 112a of the refrigerating compartment 2, so that the increase in the internal volume of the refrigerator 1 and the high energy saving performance can be achieved at the same time.

Further, by making the two

air blowers

112a and 112b different from each other, the frequency band of noise caused by the number of blades of the fan and the number of rotations can be shifted, and a rapid increase in noise generated from the refrigerator 1 and deterioration in hearing sensation can be prevented. In the present embodiment, the wind comes from the turbine windThe noise (NZ sound obtained by multiplying Z1 by N1) of the number of blades of the fan Z1 and the operating speed N1 is 183-267 s^-1Noise (NZ sound obtained by multiplying Z2 by N2) generated by the number of blades Z2 of the propeller fan and the operating speed N2 is within the range of 55-80 s^-1And (4) generating. Therefore, since the relationship of N1 × Z1 ≠ N2 × Z2 that is different between the two frequency bands is established, it is possible to prevent a sudden increase in noise and deterioration in the auditory sensation.

In addition, the noise (2NZ sound) of multiples of NZ sound is 367-533 s in the turbo fan^-1In the propeller fan, the temperature is 110 to 160s^-1. Therefore, when the generation range of the 2NZ sound is included in addition to the 1NZ sound, since the frequency bands generated by the two air-sending

devices

112a and 112b are different, it is possible to further prevent a sudden increase in noise and deterioration of the auditory sensation. The frequency bands of the turbo fan and the propeller fan are compared using an average value for a certain period of time or longer, and do not prevent the frequency bands from being instantaneously matched.

Fig. 12 is a sectional view of a case where the turbofan according to the embodiment is vertically mounted. As shown in fig. 12, in the refrigerator of the present embodiment, a turbo fan as a blower 112a is arranged substantially vertically. The front-side end of the blower 112a is located on the rear side of the front-side end of the evaporator 105 a. The vertical projection of the blower 112a overlaps at least a part of the vertical projection of the evaporator 105a, and in the present embodiment, the vertical projection of the blower 112a is disposed so as to be included in the vertical projection of the evaporator 105 a.

In the present embodiment, the turbofan has 10 blades, and the diameter of the blade is set to 100mm, which is about 1100-1600 min^-1The rotational speed of (3) is operated. Since the turbo fan has a characteristic of blowing out a flow sucked in the axial direction in the radial direction, a large space is not required between the blower 112a and the back surface of the refrigerator 2. Accordingly, the depth 30 of the air passage in the portion where the blower 112a is disposed (the periphery of the blower 112 a) can be made equal to the depth 31 of the evaporator 105a without impairing the air blowing efficiency, and thus can contribute to an increase in the internal volume. The term "equivalent" as used herein means that the air blower 112a is disposed at a position facing the front sideThe distance from the rear surface side of the partition 40 to the front surface side of the inner case 10b (the depth 30 of the air passage around the air blower 112 a) is within ± 20%, preferably within ± 10%, of the depth 31 of the evaporator 105 a. In the case where the partition 40 is not straight in the vertical direction, the depth dimension 30 of the air passage is an average of the height ranges from the upper end to the lower end of the blower 112 a.

In the present embodiment, since the blower 112a and the casing 17 are provided above the evaporator 105a, the temperature of the lower side is lower than that of the upper side of the refrigerating compartment 2. Therefore, when the fan is stopped, the air flows downward from above due to natural convection, so that the cold air in the subzero temperature zone around the evaporator 105a does not easily flow to the blower 112a and the casing 17, and dew condensation water adhering to the turbofan and the casing does not easily freeze, and frost, or the like does not easily grow. Therefore, even when the fan is moved again, operational failure due to frost or freezing is unlikely to occur.

As shown in fig. 12, the lower surface 17a of the housing 17 is provided with an opening 21. The opening 21 has a slope of an inclination angle α (in the present embodiment, the inclination angle is 1 °) so as to be the lowermost portion of the housing 17. By providing the opening 21 in the lowermost portion of the housing 17 in this manner, dew condensation water accumulated in the housing can be discharged. And, the drainage performance is improved by setting the slope of the lower surface 17a of the housing.

A turning wall 21a (air passage resistance adding means) for increasing the air passage resistance by curving the flow is provided in the communication passage 33 from the opening 21 to the evaporator chamber 16 a. When the blower 112a is driven, air leaks from the opening 21. Therefore, a part of the air sucked from the inlet 17b and boosted in pressure by the blower 112a flows from the opening 21 to the evaporator chamber 16a via the communication passage 33 without going to the output air passage 18a, returns to the inlet 17b again, and is boosted in pressure (the flow indicated by the broken line in fig. 12). This flow reduces the amount of air circulating in the refrigerating chamber 2, and the energy saving performance is reduced.

As shown in fig. 12, in order to increase the resistance of the communication flow path 33, the refrigerator of the present embodiment includes a turning wall 21a as an air path resistance adding mechanism. By providing such duct resistance adding means, the volume of air output through the opening 21 is reduced, and a decrease in energy saving performance can be suppressed. The air passage resistance adding mechanism may be another mechanism if the air passage resistance is not increased as compared with the case where the opening 21 is provided in the wall surface to allow the air to directly flow out to the evaporator chamber 16 a. For example, although the air passage resistance can be increased by increasing the distance of the communication flow passage 33, the communication flow passage 33 can be formed in a short length by increasing the air passage resistance by bending the flow by the turning wall 21a as in the refrigerator of the present embodiment, and the risk of freezing in the communication flow passage 33 can be reduced.

A part of the turning wall 21a is provided on the front surface side of the communication flow path 33 as a directional flow path that blocks the forward output toward the inflow port 17 b. This increases the resistance until the air output to the evaporator chamber 16a reaches the inlet 17b, and is less likely to be drawn into the inlet 17b, so that the air volume of the air output through the opening 21 decreases, and a decrease in energy saving performance can be suppressed.

Fig. 13 is a cross-sectional view C-C of fig. 12. The casing 17 is provided with a blower 112 a. By rotating the blower 112a clockwise (in the direction of the solid line arrow in fig. 13), air flows toward the output air duct 18a as indicated by the broken line arrow in fig. 13. A part of the air flows out to the evaporator chamber 16a through the opening 21. The communication flow path 33 below the opening 21 serves as a directional flow path that outputs air from the turning wall 21a to the right direction in fig. 13. Accordingly, the direction of the circulation flow of the air output from the opening 21 in the rotation direction of the blower 112a is output while being substantially 180 degrees turned, and therefore the air passage resistance of the communication flow passage 33 is increased, the flow of the air leaking from the opening 21 is reduced, and the reduction in the energy saving performance can be suppressed.

As shown in fig. 13, a tongue portion 17c serving as a starting point of the expanded flow path in an eddy flow shape is provided at the lower end of the side wall of the output air passage 18a of the casing 17 on the blower 112a side. If Lf is the blade width of the fan and Lk is the width from the tongue 17c to the right end of the housing 17 with the fan interposed therebetween, Lf is configured to fall within the range of Lk. This prevents dew condensation water from adhering to the blades of the fan 112a when dew condensation water generated in the outlet duct 18a and the outlet 19a (shown in fig. 2) flows down by gravity and drips down from below the tongue portion 17 c. Namely, the following refrigerator is obtained: the reliability is high because the air blowing performance is not easily lowered due to freezing between the blades, and abnormal noise is not easily generated due to contact between the grown ice and the casing 17.

The minimum width 60 (about 6mm in the present embodiment) of the communication flow path 33 from the opening 21 to the evaporator chamber 16a and the minimum width 61 (about 6mm in the present embodiment) between the blades of the blower 112a are larger than the average stacking interval Pf1 (3 mm in the present embodiment, shown in fig. 6) of the fins of the evaporator 105 a. Since the refrigerating compartment 2 is configured according to the dimensional relationship described above, when frost grows, the fins of the evaporator 105a are most likely to be clogged. Therefore, the defrosting operation is performed so as to avoid clogging between the fins of the evaporator 105a, and the refrigerator is configured as follows: the communication passage 33 having a relatively large width and the inter-blade clogging are less likely to occur, and the reliability is high.

Fig. 14 shows an example of the operation mode of the present embodiment. Here, the case where the temperature of the outside air is high (for example, 32 ℃) and the humidity is not low (for example, 60% RH) is shown. Time t₀This is the time when the refrigerating operation for cooling refrigerating room 2 is started. In the cooling operation, the three-way valve 107 is set to the outlet 107a side, and the compressor 100 is driven to cause the refrigerant to flow to the evaporator 105a, thereby lowering the temperature of the evaporator 105 a. In this state, the blower 112a is operated to cool the refrigerating compartment 2 by the air having a low temperature passing through the evaporator 105 a. Here, the temperature of the evaporator 105a in the cooling operation is higher than that of the evaporator 105b in the freezing operation described later. Generally, the higher the temperature of the evaporator, the higher the COP (the ratio of the amount of heat cooled to the input of the compressor 100) and thus the higher the energy saving performance. Therefore, the temperature of evaporator 105a is increased (e.g., -6 deg.C) to improve energy saving performance, as compared to freezing chamber 7, which requires the temperature of evaporator 105b to be changed to a low temperature (e.g., -25 deg.C). In the refrigerator 1 of the present embodiment, the rotational speed of the compressor 24 in the cooling operation is setThe temperature is lower than that in the freezing operation so that the temperature of the evaporator 105a in the cooling operation is higher than that of the evaporator 105b in the freezing operation.

Cooling the refrigerating chamber 2 by a refrigerating operation if the temperature of the refrigerating chamber is lowered to T_Roff(time t)₁) Then, the refrigeration operation is switched to the refrigerant recovery operation. In the refrigerant recovery operation, the compressor 100 is driven with the three-way valve 107 fully closed, and the refrigerant in the evaporator 105a is recovered. This suppresses the shortage of refrigerant in the next freezing operation. Further, by driving the air blower 112a at this time, the residual refrigerant in the evaporator 105a can be effectively used for cooling the refrigerating compartment 2, and the refrigerant in the evaporator 105a is easily evaporated and reaches the compressor 100, so that a large amount of refrigerant is collected in a short time, and the cooling efficiency can be improved.

When the refrigerant recovery operation is finished (time t)₂) Then, the operation is switched to the freezing operation for cooling the freezing chamber 7. In the freezing operation, the three-way valve 107 is set to the outlet 107b side, and the refrigerant flows into the evaporator 105b to lower the temperature of the evaporator 105 b. In this state, the blower 112b is operated to cool the freezing chamber 7 by the air having a low temperature by the evaporator 105 b. The freezing operation is performed until the temperature of the freezing chamber reaches T_Foff(time t)₅). During the freezing operation, a vegetable compartment damper (not shown) is also opened to cool the vegetable compartment 6 until the vegetable compartment temperature is T_Roff(time t)₃)。

In the refrigerator 1 of the present embodiment, the defrosting operation of the evaporator 105a is performed in the freezing operation. The defrosting operation of the evaporator 105a is performed by driving the blower 112 a. Since the refrigerant does not flow to evaporator 105a during the freezing operation, when the air in refrigerating room 2 passes through evaporator 105a, evaporator 105a and frost adhering to evaporator 105a are heated by heat exchange with refrigerating room 2 having a temperature higher than that of evaporator 105 a. The evaporator 105a is defrosted by this heating. Further, the air is cooled by the evaporator 105a and the frost attached to the evaporator 105a, and the air is blown to the refrigerating compartment 2 by the blower fan 112a, so that the refrigerating compartment 2 can be cooled. Therefore, frost adhering to evaporator 105a can be melted without using a heater, and refrigerating room 2 can be cooled, and therefore the defrosting operation of evaporator 105a of the present embodiment is a defrosting operation with high energy saving performance.

In addition to the evaporator 105a, frost and ice that have grown on the casing 17 and the blower 112a can be melted in the same manner by this defrosting operation. This defrosting operation is performed until the temperature of the evaporator 105a reaches T_DR(T in the refrigerator of the present embodiment)_DRAt 3 deg.C (time t)₄)。

When both the defrosting operation and the freezing operation of the evaporator 105a satisfy the termination condition (time t)₅) Then, the refrigerant recovery operation for driving the compressor 100 with the three-way valve 107 fully closed is performed again to recover the refrigerant in the evaporator 105b, thereby suppressing the shortage of refrigerant in the next refrigerating operation. Further, by driving the air blower 112b at this time, the refrigerant remaining in the evaporator 105b can be effectively used for cooling the freezing chamber 7, and the refrigerant in the evaporator 105b can be easily evaporated and reach the compressor 100, so that a large amount of refrigerant can be collected in a short time, and the cooling efficiency can be improved.

When it reaches time t₆Then, the operation returns to the cold storage operation again, and the above operation is repeated. The above is the basic cooling operation of the refrigerator of the present embodiment and the defrosting control of the evaporator 105 a. With the above operation, refrigerating compartment 2, freezing compartment 7, and vegetable compartment 6 are cooled and maintained at a predetermined temperature, and frost growth of evaporator 105a is suppressed.

When the end condition of the defrosting operation of the evaporator 105a is satisfied (the temperature of the evaporator 105a is T)_DR) Before, the end condition of the freezing operation is satisfied (the temperature of the freezing chamber becomes T)_Foff) In the case of (3), the compressor 100 is turned off while the defrosting operation of the evaporator 105a is maintained. After that, when the end condition of the defrosting operation of the evaporator 105a is satisfied, the compressor 100 is turned on and the operation is shifted to the cooling operation. This suppresses the frost and defrosted water adhering to the evaporator 105a, the casing 17, and the blower 112a during melting from being cooled again and refrozen during the cooling operation.

And, at time t₁And time t₂In the case of a freezer compartment temperature lower than a predetermined value, and at time t₅And time t₆When the refrigerating compartment temperature is lower than the predetermined value, the compressor 100 is stopped. This can suppress excessive cooling in the tank.

In the refrigerator of the present embodiment controlled as described above, the defrosting operation time of the refrigerating chamber (time t in fig. 14)₁～t₄) Specific cooling operation time (time t in fig. 14)₀～t₁) Long. Accordingly, the time for which the temperature rises in the air around the casing 17 and the air blower 112a can be made longer than the time for which the temperature falls, and therefore the casing 17 and the air blower 112a can be sufficiently heated without using a heater, and a refrigerator with high energy saving performance is obtained.

In the refrigerator of the present embodiment, the time for which the air around the casing 17 and the blower 112a reaches the above-zero temperature is longer than the time for which the air reaches the below-zero temperature.

In addition, in the refrigerator of the present embodiment, in the driving state of the compressor 100, the time for flowing the refrigerant to the outlet port 107b of the three-way valve is longer than the time for flowing the refrigerant to the outlet port 107a of the three-way valve. This makes it possible to make the time for which the temperature of the evaporator 105a is constant or rises within the above-zero temperature range longer than the time for which the temperature of the evaporator 105a is constant or falls within the below-zero temperature range. Therefore, the time for the temperature around the casing 17 and the blower 112a to reach the above-zero temperature can be longer than the time for the temperature to reach the below-zero temperature. Therefore, the growth of frost and ice in the casing 17 and the blower 112a can be suppressed without the heater.

In the present embodiment, the operation time of the blower 112a is configured to be longer than the stop time. This makes it difficult for water to stay in one place in the casing 17 and the blower 112a due to forced convection of air, and improves drainage.

In the refrigerator of the present embodiment, the end of the defrosting operation is determined based on the temperature of the evaporator 105a, but the defrosting operation may be continued for a predetermined time period and controlled based on the time period, so that the defrosting operation time of the refrigerating chamber may be longer than the refrigerating operation time. In the refrigerator according to the present embodiment, the average temperature of the components in the periodic control is evaluated, and the above characteristics are sufficient, and the same effect can be obtained even when the characteristics are locally or short-term different.

Fig. 15 is an enlarged view of the refrigerating compartment of fig. 3. Fig. 15 is a view of the refrigerator viewed from the back side. Therefore, the right direction in the figure shows the door 2a side, and the left direction in the figure shows the door 2b side.

As shown in fig. 15, the blower 112a includes the casing 17 in an eddy shape, and thus the flow in the entire circumferential direction blown out from the blower 112a can be efficiently guided to be concentrated in the upward direction. Further, by gradually increasing the size 32 of the output air duct perpendicular to the air flow direction in the air flow direction, the air volume of the refrigerating compartment 2 can be increased by the diffusion effect.

Further, outer box 10a as the upper surface of refrigerating room 2 in the present embodiment is in contact with the outside air, and heat insulating partition wall 12a as the lower surface of refrigerating room 2 is in contact with the freezing room, so that the upper surface side is most likely to be heated. Therefore, by providing the output port 19a in the housing 17 and opening it upward, the region most likely to be heated can be efficiently cooled. When the blower 112a is stopped, the low-temperature air in the upper portion of the refrigerating compartment 2 flows downward, and therefore the food in the compartment can be efficiently cooled.

In the present embodiment, since the blower 112a is a turbofan, even when frost grows on the surface of the evaporator 105a, low-temperature air can be supplied into the refrigerating compartment 2 with a large air volume, and the temperature in the refrigerating compartment 2 can be suitably equalized. Furthermore, evaporator 105a is for refrigerating room 2 and has a temperature higher than that of evaporator 105b for freezing room 7, and therefore, air in a state close to the refrigerating temperature range can be supplied into refrigerating room 2, which has an advantage of facilitating temperature adjustment. As a result, according to the present embodiment, the average temperature of the entire refrigerating room 2 can be kept at 3 ℃ or lower, preferably about 2 ℃ lower than the conventional temperature, and the effect of keeping the freshness in the refrigerating room 2 can be improved.

As shown in fig. 15, output air passage 18a above casing 17 is an arcuate directional air passage having a velocity component directed to the right. In general, when the blower 112a includes the casing 17 having an eddy shape, the air tends to flow toward the outer periphery of the casing 17. Therefore, the air is likely to flow to the left side of output air passage 18a, and if an output air passage extending linearly upward is formed, the output air is forced to the left side, making it difficult to cool the right side of refrigerating compartment 2. Therefore, as shown in the present embodiment, output air passage 18a is formed by a curved surface that faces the entire right side, and the air is deflected to the right side, so that the temperature of refrigerating room 2 can be made uniform. By utilizing the above-described effect of making the temperature uniform, the refrigerating chamber 2 can be cooled in a short time, and thus the energy saving performance of the refrigerator 1 can be improved.

As shown in fig. 15, heat insulator 52 is provided around output air duct 18a and casing 17, thereby preventing condensation in refrigerating compartment 2. The heat insulating material 52 is covered with a cover 53 (side view is shown in fig. 2), and the cover 53 is substantially vertical. By providing such a cover 53, when the positions of the

shelf plates

14a, 14b, and 14c are changed in the vertical direction, a gap is generated between the shelf plate and the cover 53, and food or the like does not fall through the gap, thereby providing a refrigerator having excellent usability. In the present embodiment, heat insulating material 52 is provided around output air duct 18a and casing 17, but even if the heat insulating material is partially reduced to be hollow, condensation on refrigerating compartment 2 can be similarly prevented.

As shown in fig. 15, the interior of blower 112a, casing 17, and output air passage 18a are configured to have a narrower air passage than refrigerating compartment 2 and evaporator chamber 16a, and thus have a faster air speed. In particular, the air flowing out of the evaporator 105a merges with the peripheral air passage of the fan 112a, so that the wind speed is maximized, and the casing 10 in the vicinity of the fan 112a is likely to be penetrated by heat. On the other hand, since the side heat dissipation pipes 102 are provided on the left and right sides of the casing 10, the surfaces of the inner casing 10b configured as the left and right side surfaces are more likely to be penetrated by heat than the center side.

By disposing the blower 112a substantially at the center in the left-right direction of the refrigerating compartment 2, the wind speed is reduced at a portion of the casing that is likely to be invaded by heat, and thus the heat invasion amount of the refrigerating compartment 2 can be reduced.

In the present embodiment, since the vacuum heat insulating material 11 is provided on the rear surface side of the casing 10, the outer peripheral side is more likely to be penetrated by heat than the center side on the rear surface side of the casing 10. By disposing the blower 112a substantially at the center in the left-right direction of the refrigerating chamber 2, the wind speed is reduced at a portion of the casing 10 that is likely to be invaded by heat, and thus the heat invasion amount of the refrigerating chamber 2 can be reduced.

In addition, as shown in fig. 15, the center line 45 of the evaporator 105a in the left-right direction is disposed to pass through a part of the blower 112a, so that the unevenness of the wind speed distribution of the evaporator 105a can be suppressed to the minimum, and the energy saving performance of the refrigerator 1 can be improved.

Fig. 16 is an enlarged view of a main portion of fig. 2 showing a relationship between a shelf and a blowing path of the refrigerating compartment according to the present embodiment. In the present embodiment, the internal volume of the refrigerating compartment 2 is further increased by optimizing the arrangement relationship between the air passage provided with the turbofan and the shelf. As shown in fig. 16, the refrigerator 1 of the present embodiment includes a partition 40 between the refrigerating chamber 2 and the evaporator chamber 16a, and is arranged such that an upper surface 41 of the partition and an upper surface of the shelf 14c are substantially horizontal and have substantially the same height as each other. This allows the upper surface 41 of the partition to be used as an extension of the shelf 14c, thereby increasing the internal volume.

In the present embodiment, the upper surface 41 of the partitioning member is brought into contact with the upper surface of the shelf 14c in order to improve space efficiency, but a minute gap may be present without contact. The separator 40 is substantially vertically configured. Accordingly, when the shelf 14c is moved downward, the gap between the shelf 14c and the partition 40 is minimized, and the shelf 14c can be moved according to the food to be stored, so that the usability of the refrigerator 1 is improved. In the present embodiment, the entire area of the partition 40 is made substantially vertical, but the same effect can be obtained also in a configuration in which only the partition 40 above the shelf 14d or above the fresh air compartment 15 is made substantially vertical.

Here, a method of mounting the blower 112a as a centrifugal fan to the casing 17 will be described with reference to fig. 17 to 19. As shown in fig. 19, the centrifugal fan of the present embodiment includes: a cylindrical rotating body 71 having blades; a cylindrical support portion 72 that supports the rotating body 71; and a housing 17 accommodating the above components. The support portion 72 extends in the outer shape direction at three circumferential positions, and circular rubber mounts 73 are attached to these portions.

Each rubber holder 73 is positioned in the rotational direction and the front-rear direction by the first locking portion 17d and the second locking portion 17e shown in fig. 18. The first locking portion 17d faces the side surface and the front surface of the rubber holder 73, and the second locking portion 17e faces the side surface and the rear surface of the rubber holder 73.

Fig. 17 (a) shows a state in the middle of the attachment of the rubber holder 73, and fig. 17 (b) shows a state in which the attachment of the rubber holder 73 is completed. Each rubber mount 73 has a first engaging portion 17d on one side in the rotational direction of the rotary body 71, and a second engaging portion 17e on the other side in the rotational direction of the rotary body 71.

As shown in fig. 17 (a), first, one of the rubber mounts 73 is fitted to the first locking portion 17d and the second locking portion 17e in order 1. Next, another rubber holder 73 is placed on (before) the second locking portion 17e in order 2. In addition, in the sequence 3, the other rubber holder 73 is pressed against the second locking portion 17e, the second locking portion 17e is bent rearward, and in this state, the other rubber holder 73 is rotated in the arrow direction with the one rubber holder 73 as a fulcrum. As shown in fig. 17 (b), the other rubber holder 73 is also fitted into the first locking portion 17d, and the mounting is completed. When the housing 17 is attached to the refrigerator, the first locking portion 17d cannot be bent by the inner wall of the refrigerator, and the rubber holder 73 does not fall off from the first locking portion 17d even if strong impact or vibration is applied by transportation or the like.

Since the support portion 72 and the housing 17 are fixed to the outside of the rotating body 71 via the rubber mount 73 in this way, the fixing operation can be easily performed from the outside of the rotating body 71, and the centrifugal fan can be prevented from being enlarged in the front-rear direction. Further, since the support portion 72 can be easily fixed to the housing 17 without using screws or the like, workability is improved, and the number of components can be prevented from increasing. Further, since the rubber mount 73 is not fastened with screws or the like, it is easy to prevent the occurrence of noise due to the transmission of the vibration of the blower 112a to the casing 17. Further, as shown in fig. 19, since the front end of the first locking portion 17d is located rearward of the rear end of the blade of the rotor 71, the first locking portion 17d does not become an obstacle to the air blown out in the radial direction from the gap of the blade, and a decrease in fan efficiency can be suppressed.

The above is the mode of the present embodiment. The present invention is not limited to the above embodiment, and includes various modifications. For example, the above-described embodiments have been described in detail to explain the present invention easily and understandably, and are not necessarily limited to having all the structures described. Further, a part of the configuration of the embodiment can be added, deleted, or replaced with another configuration.

Claims

1. A refrigerator is provided with: a first storage compartment for refrigerating the temperature zone; a second storage compartment for freezing the temperature zone; a first evaporator for cooling the first storage chamber; a second evaporator for cooling the second storage chamber; a first blower for blowing air cooled by the first evaporator; and a second blower for blowing the air cooled by the second evaporator,

the above-mentioned refrigerator is characterized in that,

the first blower is a centrifugal fan disposed at a position higher than the first evaporator,

the centrifugal fan comprises: a rotating body having blades; a support portion for supporting the rotating body; and a housing accommodating the rotating body and the supporting portion,

the front end of the shell is positioned at the rear part compared with the front end of the first evaporator,

the support part and the housing are fixed to the outside of the rotating body via a rubber mount,

the rubber seat is a circular member provided in a plurality of circumferential directions on the support part,

the housing has: a first locking portion facing a side surface and a front surface of the rubber holder; and a second locking part opposite to the side surface and the back surface of the rubber seat,

wherein each of the rubber mounts is provided with the first engaging portion on one side in a rotational direction of the rotating body and the second engaging portion on the other side in the rotational direction of the rotating body, that is, each of the rubber mounts is located between the first engaging portion and the second engaging portion in the rotational direction,

the second locking portion is bent when pressed in the rotational direction.

2. The refrigerator according to claim 1,

in the plurality of rubber mounts, in a state where one of the rubber mounts is fitted to the first engaging portion and the second engaging portion, the other rubber mount is pressed against the second engaging portion, and the other rubber mount is rotated about the one rubber mount as a fulcrum, so that the other rubber mount is fitted to the first engaging portion.

3. The refrigerator according to claim 1 or 2,

the front end of the first locking portion is located behind the rear end of the blade.