JP7028661B2 - refrigerator - Google Patents

Description

The present invention relates to a refrigerator.

As background techniques in this technical field, there are Japanese Patent Application Laid-Open No. 2014-40967 (Patent Document 1) and Japanese Patent Application Laid-Open No. 2003-322451 (Patent Document 2).

In Patent Document 1, the outer shell of the main body is composed of a heat insulating box body, and the internal space (that is, the inside of the refrigerator) of the heat insulating box body is provided with a refrigerator compartment, a freezer compartment, and a vegetable compartment from above, and is a freezer compartment. On the back side, a refrigerator equipped with a cooler and an in-compartment fan (blower means) for supplying the cold air generated by the cooler to the storage chamber is disclosed (see, for example, FIG. 2 of Patent Document 1). ..

In Patent Document 2, the outer shell of the main body is composed of a heat insulating box body, and the internal space (that is, the inside of the refrigerator) of the heat insulating box body is provided with a refrigerating room, a cooling cooking room, a vegetable room, and a freezing room from above. On the back side of the refrigerating room, a refrigerating room evaporator and a refrigerating room fan that supplies the cold air generated by the refrigerating room evaporator to the refrigerating room and the cooling cooking room are provided, and the back side of the freezing room. Is equipped with a freezer room evaporator and a freezer room fan that directly supplies the cold air generated by the freezer room evaporator to the freezer room, and the vegetable room is provided through a partition wall between the freezer room and the refrigerating room. A refrigerator that is indirectly cooled by heat transfer is disclosed (see, for example, FIG. 4 of Patent Document 2).

Japanese Unexamined Patent Publication No. 2014-40967

Japanese Patent Application Laid-Open No. 2003-322451

The refrigerator described in Patent Document 1 is configured to cool a plurality of storage chambers with one cooler. For this reason, if the evaporation temperature of the cooler when cooling the refrigerator compartment is set high, the freezer compartment will be warmed up, so the evaporation temperature of the cooler cannot be set high, in other words, the compressor can be rotated at a low speed. However, the problem was the deterioration of energy saving performance.

The refrigerator described in Patent Document 2 is provided with separate evaporators in the refrigerating chamber and the freezing chamber. Therefore, since the evaporation temperature when cooling the refrigerating chamber is set low, it is possible to operate the compressor with high efficiency and save energy. However, in the refrigerator described in Patent Document 2, a refrigerating chamber fan is provided in the refrigerating chamber which is the uppermost storage chamber. Generally, in a refrigerator having a plurality of storage chambers in the vertical direction, the uppermost storage chamber is close to the height of the user's (standing) ear. Therefore, when arranging the fan in the uppermost storage chamber, it is necessary to give sufficient consideration to quietness and avoid causing discomfort to the user. However, although the refrigerator described in Patent Document 2 is provided with a fan in the uppermost storage chamber, there is a problem that the user is likely to feel uncomfortable because the consideration for quietness is not sufficient.

In order to solve the above problems, for example, the configuration described in the claims is adopted. The present application includes a plurality of means for solving the above problems, for example, heat dissipation of a refrigerator compartment, a freezer compartment, a vegetable compartment, a compressor, and a refrigerant compressed by the compressor and whose temperature has risen. The refrigerating chamber is provided with a heat radiating means and a depressurizing means, and the refrigerating chamber includes a first evaporator in which the decompressed and low-temperature refrigerant exchanges heat with the air inside the refrigerator, and cold air generated by the first evaporator. The refrigerating chamber is provided with a first blower for circulating the air, and a second evaporator that exchanges heat with the air inside the refrigerator for the decompressed and low-temperature refrigerant, and the second evaporator are generated. A second blower for circulating cold air is provided, the refrigerating chamber is provided at the uppermost stage, the form of the first blower is a centrifugal fan, and the width between the blades of the centrifugal fan is the first. It is characterized by being larger than the fin pitch of the evaporator .

According to the present invention, it is possible to provide a refrigerator in which the change in audibility caused by the cooling fan is small and the fluid noise is small.

Front view of the refrigerator according to the first embodiment AA sectional view of FIG. BB sectional view of FIG. Configuration diagram of the refrigerating cycle of the refrigerator according to the first embodiment Arrangement of heat dissipation means of the refrigerator according to the first embodiment Configuration diagram of the evaporator of the refrigerator according to the first embodiment Perspective view of the blower for the freezing room according to the first embodiment. (A) Cross-sectional view showing the form of the flow of the propeller fan when the air passage resistance is small, (b) Cross-sectional view showing the form of the flow of the propeller fan when the air passage resistance is large. Graph showing the relationship between the aerodynamic characteristics of the blower and the noise level Perspective view of the blower for the refrigerator compartment according to the first embodiment. (A) Cross-sectional view of sirocco fan, (b) Cross-sectional view of turbofan Graph showing the relationship between noise transmittance and door area density Graph showing the relationship between noise transmittance and frequency (A) Cross-sectional view showing a comparative example when one propeller fan is mounted vertically, (b) Cross-sectional view showing a comparative example when one propeller fan is mounted horizontally, (c) Horizontal propeller fan. Cross-sectional view showing a comparative example when one is mounted on The figure which showed the relationship between the fan aerodynamic characteristic and the resistance curve of FIG. 13 (b) and FIG. 13 (c). The figure which showed the relationship between the fan aerodynamic characteristic and the resistance curve of FIG. 13A and FIG. Cross-sectional view when the turbofan according to the first embodiment is mounted vertically. Cross-sectional view taken along the line CC of FIG. The figure which showed an example of the operation pattern of the refrigerator which concerns on Example 1. Enlarged view of the refrigerator compartment in FIG. Enlarged view of the main part of FIG. 2 showing the relationship between the shelf of the refrigerating room and the air passage according to the first embodiment. Front perspective view of the refrigerator compartment (without door) according to the first embodiment. DD cross-sectional view of FIG. Front perspective view of the refrigerating room (without door, water storage tank, chilled room, surrounding heat insulating wall) according to the first embodiment. Rear perspective view of the refrigerator (without doors and surrounding heat insulating walls) according to the first embodiment. AA sectional view of FIG. 1 according to the second embodiment. AA sectional view of FIG. 1 according to the third embodiment. Graph showing the relationship between the transmittance and the frequency of the noise according to the third embodiment.

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

Example 1 of the refrigerator according to the present invention will be described with reference to FIGS. 1 to 25.
FIG. 1 is a front view of the refrigerator according to the first embodiment. As shown in FIG. 1, the refrigerator 1 of the present embodiment is composed of a refrigerating room 2 from above, an ice making room 3 and an upper freezing room 4 arranged on the left and right sides, a lower freezing room 5, and a vegetable room 6 in this order. .. Hereinafter, the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5 are collectively referred to as a freezing chamber 7. The refrigerating room 2 is divided into left and right, and is provided with a rotary refrigerating room door 2a and a door 2b that open in a double door. It includes a door 4a, a door 5a, and a door 6a. In addition, the internal material of these plurality of doors is mainly composed of urethane. Here, the average density ρ of urethane is 50 kg / m ³ , and the average thickness of the door is 40 mm.

The height H1 of the refrigerating chamber 2 is larger than the height H2 of the freezing chamber 7 (H1> H2). When the distance from the floor to the lower ends of the door 2a and the door 2b of the refrigerator compartment 2 is H5 and the product height is H6, H5 is 800 to 1200 mm and H6 is 1700 to 2100 mm, respectively, H5 = 950 mm. , H6 = 1820 mm. As a result, the refrigerator can be used while the user is standing, which improves usability.

The freezer compartment 7 is basically a storage chamber in which the inside of the refrigerator is set to a freezing temperature zone (less than 0 ° C.), for example, about -18 ° C. on average, and the refrigerating chamber 2 and the vegetable compartment 6 have a refrigerating temperature zone (less than 0 ° C.). 0 ° C. or higher), for example, the refrigerating room 2 is a storage room having an average temperature of about 4 ° C., and the vegetable room 6 is a storage room having an average temperature of about 7 ° C. By arranging the freezing room 7 between the refrigerating room 2 and the vegetable room 6 among the storage rooms, the area of the heat insulating wall separating the freezing room 7 and the outside of the refrigerator can be minimized. The amount of heat intrusion is reduced to improve the energy-saving performance of the refrigerator 1.

2 is a sectional view taken along the line AA of FIG. 1, and FIG. 3 is a sectional view taken along the line BB of FIG. As shown in the figure, the outside and the inside of the refrigerator 1 are separated by a box body 10 formed by filling a foam insulating material (for example, urethane foam) between the outer box 10a and the inner box 10b. There is. In addition to the foam heat insulating material, a plurality of vacuum heat insulating materials 11 (dotted line in FIG. 3) are mounted on the box body 10 between the outer box 10a and the inner box 10b. Here, the vacuum heat insulating material 11 is configured by wrapping a core material such as glass wool or urethane with an outer packaging material. Since the outer packaging material contains a metal layer (for example, aluminum) to ensure gas barrier properties, heat is easily transferred to the outer peripheral side of the vacuum heat insulating material 11 due to heat conduction of the outer packaging material.

The refrigerating room 2, the upper freezing room 4 and the ice making room 3 are separated by a heat insulating partition wall 12a, and similarly, the lower freezing room 5 and the vegetable room 6 are separated by a heat insulating partition wall 12b. Further, on the front side of each storage chamber of the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5, a heat insulating partition wall 12c is provided so that air inside and outside the refrigerator does not flow through the gaps between the doors 3a, 4a, and 5a. Is provided. A plurality of door pockets 13 and a plurality of shelves 14a, 14b, 14c, 14d are provided inside the doors 2a and 2b of the refrigerating chamber 2, and are partitioned into a plurality of storage spaces. The plurality of shelves 14a, 14b, 14c, 14d are supported by a plurality of support portions (not shown) provided on the inner boxes 10b on both side surfaces. Further, since the shelves 14a, 14b, and 14c are provided with support portions at different heights, the installation heights of the shelves 14a, 14b, and 14c can be adjusted according to the stored items.

The freezing room 7 and the vegetable room 6 are provided with 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 pulled out integrally with the doors 3a, 4a, 5a, and 6a, respectively. ing.

Above the heat insulating partition wall 12a, a chilled chamber 15 set lower than the temperature zone of the refrigerating chamber 2 is provided. The chilled chamber 15 is set in a refrigerating temperature range of, for example, about 0 to 3 ° C. and a freezing temperature range by controlling the evaporator 105a and the blower 112a and a heater (not shown) provided in the heat insulating partition wall 12a. For example, it is possible to switch to a mode of about -3 to 0 ° C.

The evaporator 105a is a cross-fin tube type heat exchanger for the refrigerating chamber 2, and is provided in the evaporator chamber 16a provided on the back side of the refrigerating chamber 2. The air that has become cold due to heat exchange with the evaporator 105a is refrigerated through the casing 17, the discharge air passage 18a, and the discharge port 19a that opens upward by the blower 112a provided at a position higher than the evaporator 105a. The air is blown to 2 to cool the inside of the refrigerating room 2. The air blown to the refrigerating chamber 2 returns to the evaporator 105a from the return port 20a.

Here, the form of the blower 112a is a turbofan. Further, an opening 21 is provided in the lower part of the casing 17. As a result, the dew condensation water flowing from the discharge air passage 18a is suppressed from accumulating, and the malfunction of the blower 112a is prevented.

The frost grown on the surface of the evaporator 105a on the air side can be defrosted without using a heating source such as a heater by operating the blower 112a without flowing the refrigerant through the evaporator 105a. Further, since the air blown to the refrigerating chamber 2 during the defrosting operation of the evaporator 105a is around 0 ° C. (frost temperature), the refrigerating chamber 2 can be cooled at the same time as defrosting. Therefore, in the embodiment of the present embodiment, the power consumption is lower than that of general defrosting using a heating source such as a heater, and the refrigerator compartment 2 can be cooled without operating the compressor during the defrosting operation. Even if the defrosting operation is frequently performed, the structure is such that the energy saving performance of the refrigerator 1 is not impaired.

A heater 24a is provided on the surface of the gutter 23a below the evaporator 105a. By energizing the heater 24a, even if the water accumulated in the gutter 23a freezes, the ice can be melted and drained. The melted water generated in the gutter 23a is discharged to the evaporating dish 26 provided on the upper part of the compressor 100 via the drain pipe 25a.

The evaporator 105b is a cross-fin tube type heat exchanger for the freezing chamber 7, and is provided in the evaporator chamber 16b provided on the back side of the freezing chamber 7. The air that has become cold due to heat exchange with the evaporator 105b is blown to the freezing chamber 7 through the discharge air passage 18b and the discharge port 19b by the blower 112b provided above the evaporator 105b, and enters the freezing chamber 7. Cooling. The air blown to the freezing chamber 7 passes through the freezing chamber return port 20b below the evaporator chamber 105b and returns to the evaporator 105b. Further, a propeller fan is used in the form of the blower 112b.

In the refrigerator 1 of this embodiment, the vegetable compartment 6 is also cooled by directly blowing air cooled at a low temperature by the evaporator 105b. The air in the evaporator chamber 16b, which has become cold in the evaporator 105b, is blown to the vegetable chamber 6 by the blower 112b through the vegetable chamber air passage (not shown) and the vegetable chamber damper (not shown), and is blown to the vegetable chamber 6 by the blower 112b. Cool the inside. When the temperature of the vegetable compartment 6 is low, the cooling of the vegetable compartment 6 is suppressed by closing the vegetable compartment damper. The air blown to the vegetable chamber 6 returns to the evaporator chamber 16b from the return port 20c provided in front of the lower part of the heat insulating partition wall 12b via the return air passage 22.

A heater 24b is provided below the evaporator 105b. By energizing the heater 24b, the frost grown on the air-side surface of the evaporator 105b can be melted, so that deterioration of the cooling performance of the evaporator 105b can be suppressed. The melted water generated during defrosting falls into a gutter 23b provided in the lower part of the evaporator chamber 16b, and is discharged to an evaporating dish 26 provided in the upper part of the compressor 100 in the machine room 114 via the drain pipe 25b. ..

Inside the cover 27 provided on the upper surface of the refrigerator 1, a temperature / humidity sensor 28 for detecting the temperature and humidity of the outside air is provided. A control board 29 is arranged on the upper back side of the refrigerator 1, and the refrigerating cycle and the air blowing system are controlled according to the control means stored in the control board 29.

FIG. 4 is a block diagram of the refrigerating cycle of the refrigerator according to the first embodiment. The refrigerator 1 of this embodiment is a compressor 100 that compresses the refrigerant, an external radiator 101 and a side heat dissipation pipe 102 that are heat dissipation means, a front heat radiation pipe 103, capillary tubes 104a and 104b that reduce the pressure of the refrigerant, and a heat absorbing means. Evaporators 105a and 105b, gas-liquid separators 106a and 106b to prevent liquid refrigerant from flowing into the compressor 100, three-way valve 107 to control the refrigerant flow path, check valve 108 to prevent backflow of refrigerant, and a refrigeration cycle. A dryer 109 for removing water from the inside and a refrigerant merging portion 110 for connecting a refrigerant flow path are provided, and by connecting these with a refrigerant pipe 111, the refrigerant is circulated to form a refrigerating cycle. Here, the evaporator 105a causes air to flow through the blower 112a, and the evaporator 105b causes air to flow through the blower 112b to promote cooling of the refrigerating chamber 2 and the freezing chamber 7. Similarly, the outside radiator 101 causes air to flow through the blower 113 to promote heat dissipation from the refrigerator 1.

The refrigerant discharged from the compressor 100 flows in the order of the outside radiator 101, the side heat dissipation pipe 102, the front heat dissipation 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 107b.

In the refrigerating mode in which the refrigerant flows to the outlet 107a, the refrigerant flows in the order of the capillary tube 104a, the evaporator 105a, the gas-liquid separator 106a, and the refrigerant merging portion 110, and then returns to the compressor 100. The low-pressure and low-temperature refrigerant flows through the evaporator 105a in the capillary tube 104a, and the evaporator 105a and the air in the refrigerating chamber 2 exchange heat to cool the stored items in the refrigerating chamber 2.

In the refrigerating mode in which the refrigerant flows to the outlet 107b, the refrigerant flows in the order of the capillary tube 104b, the evaporator 105b, the gas-liquid separator 106b, the check valve 108, and the refrigerant merging portion 110, and then returns to the compressor 100. Here, the check valve 108 is arranged so that the refrigerant does not flow from the refrigerant merging portion 110 to the gas-liquid separator 106b side. The low-pressure and low-temperature refrigerant in the capillary tube 104b flows through the evaporator 105b, and the evaporator 105b and the air in the freezer chamber exchange heat to cool the stored items in the freezer chamber 7.

FIG. 5 shows the arrangement of the heat radiating means of the refrigerator according to the first embodiment. The outside radiator 101 (not shown) is a fin tube type heat exchanger arranged in the machine room 114, the side heat dissipation pipe 102 is a heat dissipation pipe arranged along the side wall surface of the refrigerator 1, and the front heat dissipation pipe 103 is. It is a heat dissipation pipe arranged inside the front edge of the heat insulating partition walls 12a, 12b, 12c (see FIG. 2) of the refrigerator 1. Further, the side heat dissipation pipe 102 is embedded in the outer box 10a side in the box body 10 of the refrigerator 1. The front heat dissipation pipe 103 is embedded in the front side of the refrigerator 1 such as heat insulating partition walls 12a, 12b, and 12c (see FIG. 2) that divide each storage chamber. Further, the front heat dissipation pipe 103 not only dissipates heat, but also has a role of preventing dew condensation on the heat insulating partition walls 12a, 12b, and 12c.

6A and 6B are configuration diagrams of the evaporator of the refrigerator according to the first embodiment, FIG. 6A shows a configuration diagram of a refrigerating evaporator, and FIG. 6B shows a configuration diagram of a freezing evaporator. As shown in FIG. 6, the evaporator 105a and the evaporator 105b are cross-fin tube type heat exchangers, and are configured such that a plurality of aluminum fins 115 are penetrated by a heat transfer tube 116 bent a plurality of times. Has been done. In this embodiment, the relationship between 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 is configured to be Pf1 ≦ Pf2, and further, the height H3 of the evaporator 105a and evaporation. The relationship between the height H4 of the vessel 105b is configured to be H3 ≦ H4, and the relationship between the width W1 of the evaporator 105a and the width W2 of the evaporator 105b is configured to be W1 ≦ W2. As a result, the evaporator 105b can suppress the blockage of the flow on the air side due to frost growth while securing the heat transfer area, and the energy saving performance of the refrigerator 1 is improved by reducing the number of times the heater 24b is energized. On the other hand, since the evaporator 105a that can defrost without using a heater can be miniaturized while securing the heat transfer area, the internal volume of the refrigerating chamber 2 is increased without impairing the energy saving performance.

In this embodiment, Pf1 is set to 3 mm and Pf2 is set to 5 mm, but even in cases other than the dimensions used in this embodiment, the same effect can be obtained if the relationship of Pf1 ≦ Pf2 is established.

FIG. 7 is a perspective view of the freezer blower according to the first embodiment. In this embodiment, the blower 112b has three blades, the blade diameter is 110 mm, there is little food in the refrigerator, and the evaporator 106b is operated at a rotation speed of about 1100 to 1600 min ^-1 under normal conditions with little frost growth. ing. By operating the blower 112b, air is blown in the axial direction from the suction side to the blow side of the fan.

As shown in FIG. 2, the freezing chamber 7 has a shorter vertical distance than the refrigerating chamber 2 (H1> H2), and the evaporator 105b provided in the freezing chamber 7 has a vertical direction as compared with the evaporator 105a provided in the refrigerating chamber 2. Since the distance is long (H4> H3), the path from the evaporator to the discharge port is short. Therefore, the air discharged from the fan is discharged toward the front side of the freezing chamber 7. In such a front blowout air passage, the arrangement of the discharge air passage 18b and the discharge port 19b can be simplified by using a propeller fan having the same suction and blow directions as the mounting form of the fan, and the freezing chamber 7 can be arranged. The air volume can be increased by reducing the air passage resistance.

Further, by using a propeller fan having a wide inter-blade pitch (small number of blades) as in this embodiment, the blower 112b can be used even in a constant negative temperature zone such as a freezer chamber 7. The malfunction of the refrigerator 1 caused by the growth of frost is less likely to occur.

In this embodiment, the blower 112a is mounted in the uppermost storage chamber (refrigerator chamber). .. Generally, a propeller fan is used in a refrigerator as shown in the patent document. The propeller fan has the characteristic that noise and audibility change easily when the wind passage resistance fluctuates. Therefore, the blower 112a, which is a sound source close to the height of the user's (standing) ear in front of the refrigerator, may cause discomfort to the user. In order to solve the above problems, the mode of 112a is a turbofan in this embodiment, and the reason will be described with reference to FIGS. 8 to 11.

FIG. 8A is a cross-sectional view showing the form of the flow of the propeller fan when the air passage resistance is small, and FIG. 8B is a cross-sectional view showing the form of the flow of the propeller fan when the air passage resistance is large. In this embodiment, since the air passage is independent in the refrigerating chamber 2, the resistance is small and easy to suppress because the air passage distance is short. Therefore, under normal conditions where there is little food in the refrigerator and there is little frost growth in the evaporator, the air passage resistance is relatively small, and the flow of the propeller fan is often axial as shown in FIG. 8 (a). .. On the other hand, in a high load state where there is a lot of food in the refrigerator and there is a lot of frost growth in the evaporator, the resistance of the air passage is relatively large, and the flow of the propeller fan may become centrifugal as shown in FIG. 8 (b). many.

FIG. 9 is a graph showing the relationship between the aerodynamic characteristics of the blower and the noise level. As shown in the figure, under normal conditions where there is little food in the refrigerator and there is little frost growth in the evaporator, the air volume is relatively large and the noise level is low. On the other hand, in a high load state where there is a lot of food in the refrigerator and there is a lot of frost growth in the evaporator, the air volume is relatively small and the noise level is high.

Due to the characteristics of the propeller fan as described above, it has been a problem that the user is likely to feel uncomfortable due to changes in noise and audibility.

FIG. 10 is a perspective view of the refrigerator blower according to the first embodiment. A turbofan is used in the embodiment of the blower 112a for the refrigerator compartment 2 in this embodiment. As shown in the figure, when the turbofan is operated, wind is sucked from the axial direction of the turbofan, is carried to the outer peripheral side by centrifugal force, and is blown from the outer peripheral side to the entire circumference.

Compared to propeller fans, turbofans have the characteristic of easily increasing the air volume at high static pressure (large air passage resistance), in other words, the characteristics of less decrease in operating air volume and less increase in noise at high static pressure. .. In addition, since the form of the flow does not change significantly due to the fluctuation of the operating air volume, the change in the sense of hearing is small depending on the operating air volume.

Therefore, even when the resistance increases due to the food being put into the refrigerator chamber 2 and the air passage narrows, or the resistance increases due to the growth of frost in the evaporator 105a, the noise of the blower 112a increases and the audibility changes. Even when the blower 112a is installed at a position close to the ear level of the user (standing position) in front of the refrigerator (door side), it is possible to reduce the discomfort to the user. ..

In this embodiment, the form of the blower 112a is a turbofan, but even when a sirocco fan is used, the form of the flow does not easily change when the operating point fluctuates, so that the change in audibility can be suppressed in the same manner as the turbofan. On the other hand, focusing on the absolute value of the noise generated by the fan, the turbofan is smaller.

11A is a cross-sectional view of a sirocco fan, and FIG. 11B is a cross-sectional view of a turbofan. As shown in FIG. 11 (a), the sirocco fan has wings arranged forward with respect to the direction of flow. Due to the characteristics of the blades, the wind speed is higher than that of a turbofan because the direction of flow is small, and noise tends to increase (comparison of the same rotation speed and the same fan diameter). On the other hand, as shown in FIG. 11B, the turbofan has blades arranged backward with respect to the direction of the blowout flow. Due to the characteristics of the above-mentioned blades, the wind speed is lower than that of the sirocco fan because the direction of the flow is large, and the noise tends to be small. Therefore, by adopting a turbofan in the form of the blower 112a, even if a change in hearing sensation occurs due to a change in air passage resistance, it becomes difficult for the user to notice it, and it is possible to make it less likely to cause discomfort to the user. ..

FIG. 12 is a graph showing the relationship between the transmittance of noise and the area density of the door. The absolute value of noise can be further reduced not only by optimizing the form of the blower 112a but also by optimizing the area density of the door. The transmitted sound Lt that can be heard through the door can be obtained by the equations (1) and (2).

Here, f is the representative frequency of noise, M is the area density of the door, ρ is the average density of the door, t is the door thickness, and Li is the incident sound.

In the figure, the incident sound (sound source) is 20 dB, the representative frequency of noise is 267 Hz, the vertical axis is the ratio of the transmitted sound Lt to the incident sound Li (transmittance = Lt / Li × 100%), and the horizontal axis is the area density of the door. It is the result expressed by. The representative frequency of noise is the peak frequency of a single fan at the maximum rotation speed of the blower 112a, which is a noise level that tends to cause discomfort to the user. Further, in this embodiment, the door is made of urethane single phase, but in the case of multiple layers, the value of each layer is used as the total value. Specifically, if a steel plate or resin material is provided on the surface of urethane, the calculation is made in consideration of these as well.

From the figure, even when the sound source is near the user, the fluid sound can be reduced by about half by setting the area density of the doors (doors 2a and 2b) of the refrigerator compartment 2 to 1.5 kg / m ² or more. This makes it difficult for the user to perceive noise and changes in hearing.

In this embodiment, the representative frequency is set to 267 Hz, but the representative frequency may be different depending on the form of the fan and the maximum rotation speed. Further, if the sound insulation effect equivalent to that of this embodiment can be obtained at the representative frequency of the fan to be used, the area density does not necessarily have to be 1.5 kg / m ² or more, and the relationship of the equation (3) is satisfied. Just do it.

In this embodiment, the two blowers 112a and 112b have different forms. As a result, the peak frequency band of noise caused by the number of blades and the number of rotations of the fan can be greatly shifted, so that it is possible to prevent a sudden increase in noise generated from the refrigerating chamber 2 and deterioration of hearing sensation.

In this embodiment, the noise caused by the number of blades Z1 of the turbofan and the operating rotation speed N1 (Z1 × N1) is generated in 183 to 267s ^-1 , and the noise caused by the number of blades Z2 of the propeller fan and the operating rotation speed N2. (Z2 × N2) is generated at a frequency of 55 to 80s ^-1 . Therefore, since the relationship of N1 × Z1 ≠ N2 × Z2 in which these two peak frequency bands are different is established, it is possible not only to reduce the fluid sound distributed in a wide frequency band but also to prevent a sudden increase in noise in the peak frequency band. This makes it more difficult for the user to notice even when the noise characteristics (audibility) are changed.

Further, the noise (2NZ sound) that is a multiple of the NZ sound is 367 to 533s ^-1 for the turbofan and 110 to 160s ^-1 for the propeller fan. Therefore, even when the generation range of the 2NZ sound is included in addition to the 1NZ sound, the peak frequency bands generated from the two blowers 112a and 112b are different, so that it is possible to prevent a more rapid increase in noise. In this embodiment, the frequency bands of the turbofan and the propeller fan are compared by using the average value for a certain period of time or more during normal operation, and do not prevent the peak frequency bands from being momentarily matched. do not have.

Further, in this embodiment, the form of the blower is configured so that the relationship of N1 × Z1> N2 × Z2 is established. Blower 112a with respect to blower 112b
By increasing the peak frequency of, the noise that can be heard through the doors of the refrigerator compartment 2 (doors 2a, door 2b) is higher than the noise that can be heard through the doors of the freezer chamber (doors 3a, doors 4a, doors 5a). Can be made smaller. The reason for this will be described with reference to FIG.

FIG. 13 is a graph showing the relationship between the transmittance of noise and the frequency. The figure shows the calculation result with the incident sound (sound source) set to 20 dB. The vertical axis is the ratio of the transmitted sound Lt to the incident sound Li (transmittance = Lt / Li × 100%), and the horizontal axis is the frequency. .. From the figure, the transmittance of the propeller fan in the 1NZ range is about 100%, while the transmittance of the turbofan in the 1NZ range is 49 to 66%. Therefore, by selecting the turbofan as the form of the blower 112a of the refrigerating chamber 2, it is possible to provide a refrigerator in which the noise in the peak frequency band generated from the refrigerating chamber 2 is small. Here, in this embodiment, the thickness of the doors (doors 2a and 2b) of the refrigerating chamber 2 is 40 mm, and the average density is 50 kg / m ³ , but the same effect can be obtained even when these values are different. ..

As described above, according to the present embodiment, by selecting the turbofan as the form of the blower 112a of the refrigerating room 2, it is possible to provide a refrigerator in which the change in audibility generated from the refrigerating room 2 is small and the fluid noise is small.

In this embodiment, in addition to reducing noise, a turbofan is selected as the form of the blower 112a from a plurality of viewpoints such as improvement of blower performance, reduction of defects in the blower, and increase in the internal volume of the refrigerator compartment 2. .. Hereinafter, the reasons for using the turbofan will be described in detail with reference to FIGS. 14 to 25 in comparison with the propeller fan and the sirocco fan.

14 (a) is a cross-sectional view showing a comparative example when one propeller fan is mounted vertically, and FIG. 14 (b) is a cross-sectional view showing a comparative example when one propeller fan is mounted horizontally. (C) is a cross-sectional view showing a comparative example when one small-diameter propeller fan is mounted horizontally.

As shown in FIGS. 14 (a) to 14 (c), a propeller fan has generally been used as a blower for a refrigerator compartment.

As shown in FIG. 14A, in the form in which the propeller fan is arranged substantially vertically as the blower 112a, spaces for turning the direction of the flow are required on the front side and the back side of the propeller fan. Therefore, the depth dimension 30 of the air passage around the blower 112a becomes larger than the depth dimension 31 of the evaporator 105a, and the internal volume of the refrigerating chamber 2 tends to decrease.

In the form in which the propeller fan is arranged substantially horizontally as the blower 112a as shown in FIG. 14B, the propeller fan can operate without impairing the blowing efficiency because there is no obstacle to the flow direction, but the blower path around the blower 112a The depth dimension 30 needs to correspond to the diameter of the blower 112a. Therefore, the depth dimension 30 of the air passage around the blower 112a becomes larger than the depth dimension 31 of the evaporator 105a, and the internal volume of the refrigerating chamber 2 tends to decrease.

As shown in FIG. 14C, when the diameter D of the propeller fan is reduced as the blower 112a, the decrease in the internal volume can be suppressed, but the air volume is reduced and the energy saving performance is lowered. Therefore, in the form of FIG. 14C, when a plurality of propeller fans (for example, two) are arranged in parallel (for example, two) in the left-right direction of the refrigerator 1 as the blower 112a, the depth dimension of the blower path around the blower 112a is arranged substantially horizontally. A sufficient air volume can be secured by bringing 30 closer to the depth dimension 31 of the evaporator 105a. However, since the blowers 112a are arranged in parallel, when frost grows on the surface of the evaporator 105a and the resistance increases, the air volume tends to decrease, so that the energy saving performance may deteriorate. The reason will be described with reference to FIG.

FIG. 15 is a diagram showing the relationship between the fan aerodynamic characteristics and the resistance curve of FIGS. 14 (b) and 14 (c). The solid line is the form of FIG. 14 (b), the dotted line is the case of one propeller fan in the form of FIG. 14 (c), and the alternate long and short dash line is the case of arranging two propeller fans in parallel in the form of FIG. 14 (c). Is shown. Further, in order to make it easier to understand the characteristics, the cases where the fan rotation speeds are the same are shown here, and the operating points of each are indicated by black circles.

As shown in FIG. 15A, the resistance curve draws a gentle curve as shown in the figure because the condition is low static pressure and high air volume during normal operation in which frost does not adhere to the evaporator. When the fan diameter is reduced (dotted line) as shown in FIG. 14 (c) with respect to the form (solid line) of FIG. 14 (b), the air volume and the static pressure are reduced. Further, when two propeller fans are provided in the form of FIG. 14 (c) (dashed-dotted line), the air volume at static pressure 0 is doubled for one case. Therefore, the form of FIG. 14 (b) and the form of FIG. 14 (c) (two propeller fans) can be operated with the same air volume.

As shown in FIG. 15B, when frost grows on the surface of the evaporator, the resistance curve draws a steep curve as shown in the figure because it is a condition of high static pressure and low air volume. Therefore, in the form of FIG. 14 (c) (two propeller fans), the air volume is reduced as compared with the form of FIG. 14 (b), and the energy saving performance of the refrigerator 1 is deteriorated.

As described above, in the conventional example equipped with the propeller fan, it is a problem to expand the internal volume of the refrigerating chamber 2 while ensuring the energy saving performance, and even when the diameter and the number of the propeller fans are devised, the high static pressure is high. The problem was that the air volume was likely to decrease under low air volume conditions.

FIG. 16 is a diagram showing the relationship between the aerodynamic characteristics and the resistance curve of the propeller fan and the turbofan having the same blade diameter and the same rotation speed. As shown in FIG. 16A, in a normal state where there is little frost adhering to the evaporator 105a, it is possible to secure the same air volume when the turbofan is mounted and when the propeller fan is mounted. As shown in FIG. 16B, in a state where frost has grown on the surface of the evaporator 105a, by mounting a turbofan as in this embodiment, the air volume can be increased as compared with the case where a propeller fan is mounted. Can be done. In this embodiment, since the blower 112a is operated even when the evaporator 105a is defrosted as described above, the energy saving performance of the refrigerator 1 can be improved by improving the efficiency of the defrosting operation.

Further, as a form of a blower having a characteristic of blowing out a flow sucked in the axial direction in the radial direction as in the present embodiment, there is a sirocco fan in addition to the turbo fan used in the present embodiment. Generally, among these forms, the turbofan has a small number of blades. By using a turbofan with a small number of blades, the air flow is less likely to be blocked due to the growth of frost between the blades.

As described above, according to the present embodiment, by selecting the propeller fan as the form of the blower 112b of the freezing chamber 7 and the turbofan as the form of the blower 112a of the refrigerating chamber 2, the internal volume of the refrigerator 1 is increased and increased. It can achieve both energy saving performance.

FIG. 17 is a cross-sectional view when the turbofan according to the first embodiment is mounted vertically. As shown in FIG. 17, in the refrigerator of this embodiment, the turbofan is arranged substantially vertically as the blower 112a. Further, the front end of the blower 112a is located on the back side of the front end of the evaporator 105a. At least a part of the vertical projection of the blower 112a and the vertical projection of the evaporator 105a overlap each other, and in this embodiment, the vertical projection of the blower 112a is included in the vertical projection of the evaporator 105a. ..

In this embodiment, the turbofan has 10 blades and a blade diameter of 100 mm, and is operated at a rotation speed of about 1100 to 1600 min ^-1 during normal operation. Since the turbofan has a characteristic of blowing out the 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. As a result, the depth dimension 30 of the air passage in the portion where the blower 112a is arranged (around the blower 112a) can be made equal to the depth dimension 31 of the evaporator 105a without impairing the ventilation efficiency, which contributes to an increase in the internal volume. can do. Here, "equivalent" means that the distance from the back side of the partition 40 facing the front side of the blower 112a to the front side of the inner box 10b (depth dimension 30 of the air passage around the blower 112a) is the evaporator. It means that it is within ± 20%, preferably within ± 10% with respect to the depth dimension 31 of 105a. When the partition 40 is not straight in the vertical direction, the depth dimension 30 of the blower path is an average in the height range from the upper end to the lower end of the blower 112a.

Further, in this embodiment, since the blower 112a and the casing 17 are provided above the evaporator 105a, the temperature on the lower side of the refrigerating chamber 2 is lower than that on the upper side. Therefore, when the fan is stopped, air flows from the upper side to the lower side due to natural convection, so that it is difficult for cold air in the negative temperature zone around the evaporator 105a to flow in the blower 112a and the casing 17, and dew condensation adhering to the turbofan and the casing. Phenomena such as freezing of water, frost formation and frost growth are unlikely to occur. Therefore, even when the fan is moved again, malfunctions due to frost formation and freezing are less likely to occur. Further, since the frost that has grown upward in the evaporator 105a is blocked by the casing 17, malfunctions due to contact of the frost with the blower 112a are less likely to occur.

As shown in FIG. 17, the lower surface 17a of the casing 17 is provided with an opening 21. Further, an inclination angle α (inclination angle 1 ° in this embodiment) is provided so that the opening 21 is at the lowermost part of the casing 17. By providing the opening 21 at the lowermost portion of the casing 17 in this way, the dew condensation water accumulated in the casing can be drained. Further, the drainage performance is improved by inclining the lower surface 17a of the casing.

Further, the communication flow path 33 from the opening 21 to the evaporator chamber 16a is provided with a turning wall 21a (air passage resistance adding means) that increases the air passage resistance by bending the flow. Air leaks from the opening 21 when the blower 112a is driven. Therefore, a part of the air sucked from the inflow port 17b and boosted by the blower 112a flows from the opening 21 to the evaporator chamber 16a through the communication flow path 33 without going to the discharge air passage 18a, and flows into the evaporator chamber 16a again. It returns to 17b and is boosted (flow shown by a dotted line in FIG. 17). Due to this flow, the amount of air circulating in the refrigerating chamber 2 is reduced, and the energy saving performance is lowered.

As shown in FIG. 17, the refrigerator of this embodiment is provided with a turning wall 21a as a means for adding air passage resistance in order to increase the resistance of the communication flow path 33. By providing such a means for adding air passage resistance, the amount of air discharged through the opening 21 is reduced, and deterioration of energy saving performance can be suppressed. The air passage resistance adding means may be another means as long as the air passage resistance becomes larger than that in the case where the opening 21 is provided on the wall surface and the air is directly discharged to the evaporator chamber 16a. For example, the air passage resistance can be increased by increasing the distance of the communication flow path 33, but as in the refrigerator of the present embodiment, the air passage resistance is increased by bending the flow by the turning wall 21a. By forming the communication flow path 33 relatively short, the risk of freezing in the communication flow path 33 can be reduced.

Further, a part of the turning wall 21a is provided on the front side of the communication flow path 33, and is a directional flow path that prevents the communication flow path from being discharged forward toward the inflow port 17b. As a result, the resistance of the air discharged to the evaporator chamber 16a to the inflow port 17b increases, and it becomes difficult for the air to be sucked into the inflow port 17b. Therefore, the amount of air discharged through the opening 21 is reduced, which saves energy. It is possible to suppress the deterioration of performance.

FIG. 18 is a sectional view taken along the line CC of FIG. The blower 112a is provided in the casing 17. By rotating the blower 112a clockwise (in the direction of the solid arrow in FIG. 18), air flows toward the discharge air passage 18a as shown by the dotted arrow in FIG. Further, a part of the air passes through the opening 21 and flows out to the evaporator chamber 16a. The communication flow path 33 below the opening 21 is a directional flow path that is directed to the right in FIG. 18 and discharged by the turning wall 21a. As a result, the air discharged from the opening 21 is discharged with the direction of the circumferential flow formed in the rotation direction of the blower 112a turned by approximately 180 degrees, so that the air passage resistance of the communication flow path 33 increases and the opening By reducing the air flow leaking from the portion 21, it is possible to suppress the deterioration of the energy saving performance.

Further, as shown in FIG. 18, the casing 17 is provided with a tongue portion 17c which is a starting point of a spiral expanding flow path at the lower end of the side wall of the discharge air passage 18a on the blower 112a side. When the wingspan of the fan is Lf and the width from the tongue portion 17c to the right end of the casing 17 across the fan is Lk, the Lf is configured to be within the range of Lk. This prevents the dew condensation water generated in the discharge air passage 18a and the discharge port 19a (described in FIG. 2) from adhering to the blades of the blower 112a when it flows down due to gravity and drops from below the tongue portion 17c. be able to. That is, it is a highly reliable refrigerator that is less likely to cause deterioration of ventilation performance due to freezing between blades and generation of abnormal noise due to contact of grown ice with the casing 17.

Further, the minimum width 60 of the communication flow path 33 from the opening 21 to the evaporator chamber 16a is larger than the average stacking interval Pf1 of the fins of the evaporator 105a (3 mm in this embodiment, described in FIG. 6) (about 60 in this embodiment). 6 mm) and the minimum width 61 (about 6 mm in this embodiment) between the blades of the blower 112a are configured to be large. By configuring the refrigerating chamber 2 with the above-mentioned dimensional relationship, when frost grows, the space between the fins of the evaporator 105a is most likely to be closed. Therefore, by performing the defrosting operation so as to avoid the blockage between the fins of the evaporator 105a, the communication flow path 33 having a relatively large width dimension and the blockage between the blades are less likely to occur, and the refrigerator becomes highly reliable.

FIG. 19 is an example of the operation pattern of the refrigerator according to the first embodiment. Here, it represents a case where the outside air is relatively high temperature (for example, 32 ° C.) and is not low humidity (for example, 60% RH). Time t ₀ is the time when the refrigerating operation for cooling the refrigerating chamber 2 is started. In the refrigerating operation, the three-way valve 107 is set to the outlet 107a side, the compressor 100 is driven to flow the refrigerant through the evaporator 105a, and the temperature of the evaporator 105a is lowered. By operating the blower 112a in this state, the refrigerating chamber 2 is cooled by the air that has passed through the evaporator 105a and has become cold. Here, the temperature of the evaporator 105a during the refrigerating operation is higher than that of the evaporator 105b during the freezing operation described later. Generally, the higher the temperature of the evaporator, the higher the COP (ratio of the amount of heat to be cooled to the input of the compressor 100) and the higher the energy saving performance. Therefore, compared to the freezing chamber 7 in which the temperature of the evaporator 105b needs to be lowered (for example, −25 ° C.), the temperature of the evaporator 105a is raised (for example, −6 ° C.) to improve the energy saving performance. In the refrigerator 1 of the present embodiment, the rotation speed of the compressor 24 during the refrigerating operation is set to be lower than that during the refrigerating operation so that the temperature of the evaporator 105a during the refrigerating operation is higher than that of the evaporator 105b during the refrigerating operation. ing.

When the refrigerating chamber 2 is cooled by the refrigerating operation and the temperature of the refrigerating chamber drops to _TRoff (time t ₁ ), the refrigerating 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 to recover the refrigerant in the evaporator 105a. As a result, the shortage of the refrigerant in the next freezing operation is suppressed. At this time, the blower 112a is driven, whereby the residual refrigerant in the evaporator 105a can be utilized for cooling the refrigerating chamber 2, and the refrigerant in the evaporator 105a evaporates and easily reaches the compressor 100. Therefore, the cooling efficiency can be improved by recovering a large amount of refrigerant in a relatively short time.

When the refrigerant recovery operation is completed (time t ₂ ), 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 is passed through the evaporator 105b to lower the temperature of the evaporator 105b. By operating the blower 112b in this state, the freezing chamber 7 is cooled by the air that has passed through the evaporator 105b and has become cold. This freezing operation is performed until the freezing room temperature reaches T _Foff (time t ₅ ). In addition, the vegetable compartment damper (not shown) is also opened during the freezing operation, and the vegetable compartment 6 is cooled until the vegetable compartment temperature reaches _TRoff (time t ₃ ).

Further, in the refrigerator 1 of the present embodiment, the evaporator 105a is defrosted during this freezing operation. The defrosting operation of the evaporator 105a is performed by driving the blower 112a. Since the refrigerant is prevented from flowing into the refrigerator 105a during the refrigerating operation, when the air in the refrigerating chamber 2 passes through the evaporator 105a, the heat exchange with the refrigerating chamber 2 having a temperature higher than that of the refrigerator 105a causes the evaporator 105a. And the frost adhering to the evaporator 105a is heated. Defrosting of the evaporator 105a is performed by this heating. The air is cooled by the frost adhering to the evaporator 105a and the evaporator 105a, and this air is blown to the refrigerating chamber 2 by the blower 112a, so that the refrigerating chamber 2 can be cooled. Therefore, the frost adhering to the evaporator 105a can be melted without using a heater, and the refrigerating chamber 2 can be cooled. Therefore, the defrosting operation of the evaporator 105a of this embodiment has high energy-saving performance. It is a frost operation.

Further, by this defrosting operation, in addition to the evaporator 105a, the frost and ice grown in the casing 17 and the blower 112a can be similarly melted. This defrosting operation is performed until the temperature of the evaporator 105a reaches T _DR (T _DR = 3 ° C. in the refrigerator of this embodiment) (time t ₄ ).

When both the defrosting operation and the refrigerating operation of the evaporator 105a are satisfied (time t ₅ ), the refrigerant recovery operation for driving the compressor 100 with the three-way valve 107 fully closed is performed again, and the inside of the evaporator 105b is operated. The refrigerant is recovered and the shortage of the refrigerant in the next refrigerating operation is suppressed. At this time, the blower 112b is driven, whereby the residual refrigerant in the evaporator 105b can be used for cooling the freezer chamber 7, and the refrigerant in the evaporator 105b evaporates and easily reaches the compressor 100. Since a large amount of refrigerant can be recovered in a relatively short time, the cooling efficiency can be improved.

At time t6, the refrigerating operation is returned again, and the above _- mentioned operation is repeated. The above is the basic cooling operation of the refrigerator and the defrosting control of the evaporator 105a of this embodiment. By these operations, the refrigerating chamber 2, the freezing chamber 7, and the vegetable chamber 6 are cooled and maintained at a predetermined temperature, while suppressing the frost growth of the evaporator 105a.

If the end condition of the refrigerating operation (the temperature of the freezer chamber becomes T _Foff ) is satisfied before the end condition of the defrosting operation of the evaporator 105a (the temperature of the evaporator 105a becomes T _DR ) is satisfied. The compressor 100 is turned off while the defrosting operation of the evaporator 105a is continued. After that, if the end condition of the defrosting operation of the evaporator 105a is satisfied, the compressor 100 is turned on and the refrigerating operation is started. As a result, it is possible to prevent the frost and defrosted water adhering to the evaporator 105a, the casing 17, and the blower 112a during melting from being cooled again by the refrigerating operation and refreezing.

Further, the compressor ₁₀₀ is stopped when the freezing room temperature is lower than the predetermined value at time _t1 and time _t2 , and when the refrigerating room temperature is _lower than the predetermined value at time t5 and time t6. As a result, excessive cooling inside the refrigerator can be suppressed.

In the refrigerator of the present embodiment controlled as described above, the defrosting operation time (time t1 to t4 in the figure) of the refrigerating room is longer than the refrigerating operation time (time t0 to t1 in the figure). .. As a result, in the air around the casing 17 and the blower 112a, the time for the temperature to rise can be longer than the time for the temperature to drop, so that the casing 17 and the blower 112a can be sufficiently heated without using a heater, and the energy saving performance is high. It becomes a refrigerator.

Further, in the refrigerator of the present embodiment, the air around the casing 17 and the blower 112a is configured so that the time when the temperature becomes positive is longer than the time when the temperature becomes negative.

In addition, in the refrigerator of the present embodiment, in the driving state of the compressor 100, the time for the refrigerant to flow to the outlet 107b of the three-way valve is longer than the time for the refrigerant to flow to the outlet 107a of the three-way valve. As a result, the time for the evaporator 105a to be constant or rise in temperature in the positive temperature zone can be longer than the time for the evaporator 105a to be constant in the negative temperature zone or decrease in temperature. Therefore, the temperature around the casing 17 and the blower 112a can be longer for the positive temperature than for the negative temperature. Therefore, the growth of frost and ice in the casing 17 and the blower 112a can be suppressed without a heater.

Further, in this embodiment, the operating time of the blower 112a is configured to be longer than the stopping time. As a result, in the casing 17 and the blower 112a, water is less likely to stay in one place due to forced convection of air, so that drainage can be improved.

In the refrigerator of this embodiment, the end of the defrosting operation is determined based on the temperature of the evaporator 105a, but the defrosting operation should be controlled based on the time so as to end when the defrosting operation is continued for a predetermined time. Therefore, the defrosting operation time of the refrigerating room may be longer than the refrigerating operation time. Further, the refrigerator of the present embodiment may have the above-mentioned characteristics when the average temperature of the components in the periodic control is evaluated, and even if the characteristics are different locally or in the short term. A similar effect can be obtained.

FIG. 20 is an enlarged view of the refrigerator compartment of FIG. As shown in the figure, the blower 112a is provided with the spiral casing 17, so that the flow in the entire circumferential direction blown out from the blower 112a can be efficiently aggregated and guided in the upward direction. Further, the air volume of the refrigerating chamber 2 can be increased by the diffuser effect by gradually expanding the dimension 32 perpendicular to the air flow direction of the discharge air passage in the air flow direction.

Further, in the refrigerating chamber 2 of the present embodiment, the outer box 10a on the upper surface is in contact with the outside air, and the heat insulating partition wall 12a on the lower surface of the refrigerating chamber 2 is in contact with the freezing chamber, so that the upper surface side is most likely to warm up. It is composed. Therefore, the casing 17 is provided with a discharge port 19a and is opened upward so that the region most likely to be warmed can be efficiently cooled. Further, when the blower 112a is stopped, the low temperature air in the upper part of the refrigerating chamber 2 flows downward, so that the food in the refrigerator can be efficiently cooled.

Further, in this embodiment, since the blower 112a is a turbofan, even if frost grows on the surface of the evaporator 105a, low temperature air can be supplied into the refrigerating chamber 2 by a large amount of air, and the inside of the refrigerating chamber 2 can be supplied. Suitable for leveling the temperature. Further, since the evaporator 105a is for the refrigerating chamber 2 and has a higher temperature than the evaporator 105b for the freezing chamber 7, air in a state close to the refrigerating temperature zone can be supplied into the refrigerating chamber 2, so that the temperature can be adjusted. It has the advantage of being easy to do. As a result, according to the present embodiment, it is possible to keep the average temperature of the entire refrigerating chamber 2 at 3 ° C. or lower, preferably about 2 ° C., which is lower than the conventional one, and the effect of maintaining the freshness in the refrigerating chamber 2 is enhanced.

As shown in FIG. 20, the discharge air passage 18a above the casing 17 is a directional air passage formed in an arc shape so as to have a velocity component toward the right side. Generally, when the blower 112a is provided with the spiral casing 17, the flow tends to be reduced to the outer peripheral side of the casing 17. Therefore, since the wind tends to flow on the left side of the discharge air passage 18a, when the discharge air passage extending linearly upward is formed, the discharge air is biased to the left side, and it becomes difficult to cool the right side of the refrigerating chamber 2. Therefore, by forming the discharge air passage 18a with a curved surface that faces to the right as a whole as in the present embodiment, the wind direction can be deflected to the right and the refrigerating chamber 2 can have a uniform temperature. Due to the effect of making the temperature uniform, the refrigerator chamber 2 can be cooled in a short time, so that the energy saving performance of the refrigerator 1 can be improved.

As shown in FIG. 20, the heat insulating material 52 is provided around the discharge air passage 18a and the casing 17 to prevent dew condensation in the refrigerating chamber 2. Further, the heat insulating material 52 is covered with a decorative cover 53 (a side view is shown in FIG. 2), and the decorative cover 53 faces substantially a lead. By providing such a decorative cover 53, when the installation positions of the shelves 14a, 14b, and 14c are changed in the vertical direction, a gap is created between the shelf and the decorative cover 53, and food or the like falls from the gap. It will be an easy-to-use refrigerator. Further, in this embodiment, the heat insulating material 52 is provided around the discharge air passage 18a and the casing 17, but even when the heat insulating material is partially reduced to make it hollow, dew condensation in the refrigerating chamber 2 can be similarly prevented.

As shown in FIG. 20, the inside of the blower 112a, the casing 17, and the discharge air passage 18a are configured to have a higher wind speed because the air passage is narrower than that of the refrigerating chamber 2 and the evaporator chamber 16a. .. Among them, in particular, the peripheral air passage of the blower 112a has the highest wind speed because the outflow air from the evaporator 105a joins, and the box body 10 in the vicinity of the blower 112a easily invades heat. On the other hand, since the side heat dissipation pipes 102 are provided on the left and right sides of the box body 10, the surfaces of the inner boxes 10b on the left and right side surfaces are configured so that heat can easily penetrate from the center side.

By arranging the blower 112a substantially in the center of the refrigerating chamber 2 in the left-right direction, the wind speed can be lowered at a portion of the box where heat invades easily, so that the amount of heat invading the refrigerating chamber 2 can be reduced.

Further, in the present embodiment, since the vacuum heat insulating material 11 is provided on the back surface side of the box body 10, the outer peripheral side of the back surface side of the box body 10 has a configuration in which heat penetrates more easily than the central side. By arranging the blower 112a substantially in the center of the refrigerating chamber 2 in the left-right direction, the wind speed can be lowered at a portion of the box body 10 where heat invades easily, so that the amount of heat invading the refrigerating chamber 2 can be reduced.

In addition, as shown in FIG. 20, the center line 45 in the left-right direction of the evaporator 105a is arranged so as to pass through a part of the blower 112a. As a result, the non-uniformity of the wind speed distribution of the evaporator 105a can be minimized, so that the energy saving performance of the refrigerator 1 can be improved.

FIG. 21 is an enlarged view of a main part of FIG. 2 showing the relationship between the shelves of the refrigerating room and the air passage according to the present embodiment. In this embodiment, the food storage space of the refrigerating room 2 is expanded by optimizing the relationship between the air passage provided with the turbo fan and the arrangement of the shelves. As shown in the figure, the refrigerator 1 of this embodiment is provided with a partition 40 between the refrigerating chamber 2 and the evaporator chamber 16a, the upper surface 41 of the partition and the upper surface of the shelf 14c are substantially horizontal, and the heights of the partitions are approximately horizontal. They are arranged so that they match. As a result, the upper surface 41 of the partition can be used as an extension of the shelf 14c, so that the food storage space can be increased.

In this embodiment, the upper surface 41 of the partition and the upper surface of the shelf 14c are in contact with each other in order to improve space efficiency, but there may be a slight gap without contact. Further, the partition 40 is configured substantially vertically. As a result, 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. Therefore, the refrigerator 1 Usability is improved. In this embodiment, the entire area of the partition 40 is substantially vertical, but the same effect can be obtained even in a configuration in which only the partition 40 above the shelf 14d or above the chilled chamber 15 is substantially vertical.

FIG. 22 is a front perspective view of the refrigerator compartment (without door). The figure shows the structure excluding the doors 2a and 2b in order to visualize the internal structure. A chilled chamber 15 is provided in the lower right of the refrigerating chamber 2, a water storage tank 70 for ice making is provided in the lower left of the refrigerating chamber, and a partition 71 is provided between the chilled chamber 15 and the water storage tank 70. Further, the air return port 20a is divided into a plurality of parts, and in this embodiment, the first return port 72a is on the left side between the shelves 14c and the shelf 14d, and the first is on the right side between the shelves 14c and the shelf 14d. A return port 72b, a first return port 72c around the water storage tank 70, and a first return port 72d around the chilled chamber are provided. By providing the air return port 20a between the shelves 14c and 14d in this way, the amount of air flowing around the partition 12a between the refrigerating chamber 2 and the freezing chamber 7 is reduced. By this. The amount of heat exchanged by forced convection between the refrigerating chamber 2 and the freezing chamber 7 is reduced, and as a result, the time required for the refrigerating operation in which the compressor is operated at a relatively high rotation speed is reduced, so that the energy saving performance of the refrigerator can be improved.

In this embodiment, the mainstream of air that cools the refrigerating chamber 2 is the first return ports 72a and 72b.
The air passage is constructed so as to flow through. As a result, the air passage resistances of the first return ports 72c and 72d become relatively large, which makes it difficult for air to flow, so that the amount of heat exchanged by forced convection between the refrigerating chamber 2 and the freezing chamber 7 can be further reduced.

It should be noted that the fact that the air passage is configured so that the main flow of the air cooling the refrigerating chamber 2 flows through the first return ports 72a and 72b is measured in a state where the first return ports 72c and 72d are closed. It can be determined by comparing the temperature of the upper surface of the partition 12a with the temperature of the same position of the partition 12a measured with the first return ports 72c and 72d open. Specifically, during normal operation, the time average value of the top surface temperature of the partition 12a measured with the first return ports 72c and 72d closed, and the state where the first return ports 72c and 72d are open. If the difference in the time average values of the temperatures at the same positions of the partition 12a measured in 1 is 1 ° C. or less, it can be said that the mainstream of the air cooling the refrigerating chamber 2 flows through the first return ports 72a and 72b. In this embodiment, the sum of the air passage cross-sectional areas of the first return ports 72a and 72b is made larger than the sum of the air passage cross-sectional areas of the first return ports 72c and 72d. As a result, the air passage resistances of the first return ports 72c and 72d become relatively large, which makes it difficult for air to flow, so that the amount of heat exchanged by forced convection between the refrigerating chamber 2 and the freezing chamber 7 can be reduced more reliably.

Furthermore, by providing a plurality of first return ports between the shelves 14c and 14d and under the shelves 14d, the total opening area can be expanded as compared with the case where the first return port is one. By reducing the road resistance, the circulating air volume can be increased and the energy saving performance of the refrigerating chamber 2 can be improved.

Here, the cross-sectional area of the air passage in this embodiment refers to the area on the plane perpendicular to the air flow direction, and the air passage having the smallest area among them. Therefore, even if the opening area near the entrance of the return port is large, the cross-sectional area of the air passage is considered to be zero if a part of the air passage is blocked by a sealing material or the like.

Further, in this embodiment, the first return ports 72a and 72b are provided in order to reduce the amount of heat exchanged by the forced convection of the refrigerating chamber 2 and the freezing chamber 7. On the other hand, since it becomes difficult to heat the water storage tank 70 by forced convection, there is a possibility that a new problem may arise in which the water in the water storage tank 70 freezes. In order to solve this problem, in this embodiment, the air passage cross-sectional area of the first return port 72c is made larger than the air passage cross-sectional area of the first return port 72d. As a result, the amount of heat exchanged by forced convection between the refrigerating chamber 2 and the freezing chamber 7 can be reduced, and the water in the water storage tank can be made difficult to freeze.

FIG. 23 is a cross-sectional view taken along the line DD of FIG. As shown in the figure, the air flowing in from the first return port 72a passes through the second return port 73a, which is the opening of the evaporator chamber 16a, and returns to the evaporator 105a. Similarly, the air flowing in from the first return port 72b returns to the evaporator 105a without passing through the second return port. Further, the gutter 23a is inclined so that the distance H8 between the lower right end of the evaporator and the gutter is wider than the distance H7 between the lower left end of the evaporator and the gutter in order to drain the dew condensation water. Therefore, the air flowing in from the first return port 72a has a large air passage resistance because the distance H7 between the left lower end of the evaporator and the gutter is short, and there is a possibility that the air volume may decrease. Therefore, in this embodiment, the above problem is solved by providing a plurality of second return air passages, which will be described with reference to FIG. 24.

FIG. 24 is a front perspective view of the refrigerating room (without door, water storage tank, chilled room, and surrounding heat insulating wall). The figure shows the structure excluding the doors 2a and 2b, the water storage tank 70, the chilled chamber 15, and the surrounding insulating wall to visualize the internal structure. As shown in the figure, the evaporator chamber 16a is provided with second return ports 73a, 73b, 73c for returning air. In this way, since the opening area can be expanded by providing a plurality of second return ports, the air that has passed through the first return port 72a is less likely to shrink at the second return ports 73a, 73b, 73c, and is refrigerated. The amount of air circulating in the chamber 2 is increased, and the energy saving performance of the refrigerator 1 can be improved.

FIG. 25 is a rear perspective view of the refrigerator (without doors and surrounding heat insulating walls). As shown in the figure, an electric component box 74 is provided on the back side of the water storage tank 70. The electrical component box 74 contains, for example, a component that controls the pressure and temperature of the chilled chamber 15. By arranging the electric component box 74 on the back side of the water storage tank 70 in this way, the air passage area is wide and the space that cannot be used for storing food can be effectively used. Therefore, the energy saving performance of the refrigerator is improved and the food is stored. It is possible to expand the space at the same time.

Next, the refrigerator according to the second embodiment of the present invention will be described with reference to FIG. 26. In the second embodiment, the structures of the doors (doors 2a and 2b) of the refrigerating chamber 2 are different from those in the first embodiment. The other configurations are the same as those in the first embodiment, and duplicated description will be omitted.

FIG. 26 is a cross-sectional view taken along the line AA of FIG. As shown in the figure, the door 2a and the door 2b of the refrigerating chamber 2 are composed of urethane 65 and the vacuum heat insulating material 11. By inserting the high heat insulating layer into the door 2a and the door 2b in this way, the noise can be reduced as compared with the case where only urethane is used, and this makes it difficult for the user to notice even if the audibility is changed. .. Further, since the vacuum heat insulating material 11 has a lower thermal conductivity than the urethane 65, the amount of heat that enters the refrigerating chamber 2 from the outside air can be reduced, and the energy saving performance of the refrigerator 1 can be improved.

Next, the refrigerator according to the third embodiment of the present invention will be described with reference to FIGS. 27 to 28. In the third embodiment, the structures of the doors (doors 2a and 2b) of the refrigerating chamber 2 are different from those in the first embodiment. The other configurations are the same as those in the first embodiment, and duplicated description will be omitted.

27 is a sectional view taken along the line AA of FIG. As shown in the figure, the door 2a and the door 2b of the refrigerating chamber 2 are made of urethane 65, and further, the surface thereof is provided with a glass 66 having a thickness of 5 mm and an average density of 2500 kg / m ³ . Here, the general average density of urethane used in a refrigerator is 40 to 60 kg / m ³ , and the average density of glass is 2400 to 2600 kg / m ³ . As described above, by providing the glass 66 on the surfaces of the door 2a and the door 2b, the area density can be significantly improved as compared with the case where the door 2a and the door 2b are made of only urethane 65. Further, by making the surfaces of the door 2a and the door 2b glass 66, scratches are less likely to occur, so that the durability performance can be improved and the appearance performance can be improved.

FIG. 28 is a graph showing the relationship between noise transmittance and frequency. The figure shows the result of adding the result of the multilayer layer of urethane 65 and the glass 66 to the calculation result in the case of the urethane 65 single phase of FIG. From the figure, when the glass 66 is added to the surface of the door 2a and the door 2b by 5 mm, the transmittance in the range of 1NZ of the propeller fan is about 13 to 29%, whereas the transmittance in the range of 1NZ of the turbofan is. The rate will be 0%. Therefore, by providing glass 66 on the surfaces of the door 2a and the door 2b and selecting a turbofan as the form of the blower 112a of the refrigerating chamber 2, a refrigerator that eliminates the noise in the peak frequency band generated from the refrigerating chamber 2 is provided. can do.

In this embodiment, the thickness of the urethane 65 is 40 mm and the thickness of the glass 66 is 5 mm, but the dimensions do not necessarily have to be described, and the dimensions may be changed as long as the same effect can be obtained. ..

The above is the embodiment of this embodiment. The present invention is not limited to the above-mentioned form, and includes various modifications. For example, the above-described embodiment has been described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to the one including all the described configurations. Further, it is possible to add / delete / replace a part of the configuration of the embodiment with another configuration.

1 Refrigerator 2 Refrigerator room 3 Ice making room 4 Upper freezing room 5 Lower freezing room Freezing room 6 Vegetable room 7 Freezing room (general term for 3, 4, 5)
10 Box body 10a Outer box 10b Inner box 11 Vacuum heat insulating material 12a, 12b, 12c Insulation partition wall 13 Door pockets 14a, 14b, 14c, 14b Shelf 15 Chilled chamber 16a, 16b Evaporator chamber 17 Casing 17a Casing lower surface 17b Casing Inlet 17c Casing tongue 18a, 18b Discharge air passage 19a, 19b Discharge port 20a, 20b, 20c Return port 21 Opening 21a Turning wall (means for adding air passage resistance)
22 Return air passages 23a, 23b Gutters 24a, 24b Heaters 25a, 25b Drain pipe 26 Evaporator 27 Cover 28 Temperature sensor 29 Control board 30 Blower depth dimension 31 Depth dimension of evaporator 105a 32 Discharge air passage Dimensions perpendicular to the air flow direction 33 Communication flow path 40 Partition 41 Top surface of partition 50 Wind direction plate 52 Insulation material 53 Decorative cover 60 Minimum width of communication flow path 33 from opening 21 to evaporator chamber 16a 61 Blowers of blower 112a Minimum width between 65 Urethane 66 Glass 70 Water storage tank 71 Partition 72a First return port (between shelves, left)
72b First return port (between shelves, right)
72c First return port (around the water storage tank)
72d First return port (around the chilled room)
73a Second return port (lower left)
73b Second return port (upper right)
73c Second return port (center)
74 Electrical equipment box 100 Compressor 101 External radiator 102 Side heat dissipation pipe 103 Front heat dissipation pipe 104a, 104b Capillary tube 105a, 105b Evaporator 106a, 106b Gas-liquid separator 107 Three-way valve 108 Check valve 109 Dryer 110 Refrigerant confluence 111 Refrigerant piping 112a, 112b Blower 113 Blower 114 Machine room 115 Fin 116 Heat transfer tube

Claims (6)

A refrigerating chamber that can be set to at least a refrigerating temperature zone, a refrigerating chamber that can be set to at least a refrigerating temperature zone, a compressor, a heat radiating means that dissipates heat from a refrigerant that has been compressed by the compressor and whose temperature has risen, and a depressurizing means. The refrigerating chamber is provided with a first evaporator in which the decompressed and low-temperature refrigerant exchanges heat with the air inside the refrigerator, and a first for circulating the cold air generated by the first evaporator. A blower is provided, and the refrigerating chamber is provided with a second evaporator in which the decompressed and low-temperature refrigerant exchanges heat with the air inside the refrigerator, and a second evaporator for circulating the cold air generated by the second evaporator. A second blower is provided, the refrigerating chamber is provided at the uppermost stage, the form of the first blower is a centrifugal fan, and the width between the blades of the centrifugal fan is larger than the fin pitch of the first evaporator. A refrigerator characterized by doing. The refrigerator according to claim 1, wherein the first blower is a turbofan. In the refrigerator according to claim 1 or 2, the product of the rotation speed N1 of the first blower and the number of blades Z1 is larger than the product of the rotation speed N2 of the second blower and the number of blades Z2, N1 × Z1> N2 ×. A refrigerator characterized by having a Z2 relationship. In the refrigerator according to claims 1 to 3, when f is the peak frequency at the maximum rotation speed of the first blower, M is the area density of the door, Li is the incident sound, and Lt is the transmitted sound, the door area density is as follows. A refrigerator characterized by satisfying.

The refrigerator according to claim 1 to 4, wherein a vacuum heat insulating material is used for the material layer of the door of the uppermost storage chamber. The refrigerator according to claim 1 to 5, wherein glass is used for the material layer of the door of the uppermost storage chamber.

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