JP2019132500A - refrigerator - Google Patents

Abstract

To provide a refrigerator of high energy saving performance by suppressing heat exchange between a refrigeration chamber and a freezing chamber.SOLUTION: A refrigerator is composed of a refrigeration chamber, a freezing chamber and a vegetable chamber successively arranged from an upper portion, and includes a compressor, heat radiation means for radiating heat of a refrigerant of which a temperature is increased by being compressed by the compressor, and pressure reduction means. The refrigeration chamber is provided with an evaporator in which a refrigerant decreased in temperature by being decompressed, exchanges heat with air inside, a blower for circulating cold air generated by the evaporator, an air channel for carrying the air distributed by the blower to each of storage chambers, and a chilled chamber at a lower part of the refrigeration chamber, and a discharge port and a return port of the air channel are disposed at an upper part of the chilled chamber.SELECTED DRAWING: Figure 23

Description

  The present invention relates to a refrigerator.

As a background art in this technical field, there is JP 2014-40967 A (Patent Document 1).

  In patent document 1, the outer shell which is a main body is comprised with the heat insulation box, The interior space (namely, inside of this store | warehouse | chamber) of this heat insulation box is equipped with the refrigerator compartment, the freezer compartment, and the vegetable compartment from above, The said refrigerator compartment A refrigerator having a decompression storage chamber and an ice making water tank on the lower side, and a refrigerator and an internal fan for supplying cold air generated by the cooler to the storage chamber on the side of the freezing chamber Is disclosed (see, for example, FIG. 2 and FIG. 3 of Patent Document 2).

JP 2014-40967 A

  In the refrigerator described in Patent Document 1, a plurality of air discharge ports are provided above the decompression storage chamber, and an air return port is provided on the back side. In addition, the air circulating through the refrigerating chamber has raised the air temperature by cooling food, doors, and the like, and then the air has passed through the partition between the refrigerating chamber and the freezer compartment. For this reason, the heat exchange between the refrigerator compartment and the freezer compartment by forced convection increases the time for the freezing operation in which the compressor is operated at a relatively high speed, so the power consumption of the compressor increases and the refrigerator The problem is that energy saving performance is reduced.

In order to solve the above problems, for example, the configuration described in the claims is adopted. The present application includes a plurality of means for solving the above-mentioned problems. If one example is given, it is composed of a refrigerator compartment, a freezer compartment, and a vegetable compartment from the top. The compressor is compressed by the compressor and the temperature rises. A heat radiating means for radiating the refrigerant and a pressure reducing means are provided, and the storage chamber is provided with an evaporator for exchanging heat between the decompressed refrigerant and the low temperature and the air in the cabinet, and cold air generated by the evaporator. A blower for circulation, an air passage for carrying air blown by the blower to each storage chamber, a chilled chamber below the refrigeration chamber, and an outlet of the air passage above the chilled chamber; And a return port.

ADVANTAGE OF THE INVENTION According to this invention, the heat exchange of a refrigerator compartment and a freezer compartment can be suppressed, and a refrigerator with high energy saving performance can be provided.

Front view of the refrigerator according to the first embodiment AA sectional view of FIG. BB sectional view of FIG. The block diagram of the refrigerating cycle of the refrigerator concerning Example 1 Arrangement of heat dissipating means of the refrigerator according to the first embodiment The block diagram of the evaporator of the refrigerator which concerns on Example 1 1 is a perspective view of a freezer blower according to Embodiment 1. FIG. (A) Cross-sectional view showing the form of the propeller fan flow when the air path resistance is small, (b) Cross-sectional view showing the form of the propeller fan flow when the air path resistance is large A graph showing the relationship between the aerodynamic characteristics of a blower and the noise level 1 is a perspective view of a refrigerator blower according to a first embodiment. (A) Cross section of sirocco fan, (b) Cross section of turbo fan Graph showing the relationship between noise transmission 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 view of a small-diameter propeller fan Sectional drawing which shows the comparative example when one is mounted in The figure which showed the relationship between the fan aerodynamic characteristic and resistance curve of FIG.13 (b) and FIG.13 (c). The figure which showed the relationship between the fan aerodynamic characteristic and resistance curve of Fig.13 (a) and FIG. Sectional drawing at the time of mounting the turbo fan concerning Example 1 vertically CC sectional view 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. The principal part enlarged view of FIG. 2 which showed the relationship between the shelf of the refrigerator compartment which concerns on Example 1, and a ventilation path Front perspective view of a refrigerator compartment (no door) according to the first embodiment DD sectional view of FIG. Front perspective view of a refrigerating room (no door, water tank, chilled room, surrounding insulation wall) according to Example 1 The rear perspective view of the refrigerator (no door and surrounding heat insulation wall) according to the first embodiment AA sectional view of Drawing 1 concerning Example 2 AA sectional view of Drawing 1 concerning Example 3 The graph which shows the relationship of the transmittance | permeability of noise and frequency which concern on Example 3.

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

Embodiment 1 of a refrigerator according to the present invention will be described with reference to FIGS.
FIG. 1 is a front view of the refrigerator according to the first embodiment. As shown in FIG. 1, the refrigerator 1 of this embodiment is comprised from the upper part in the order of the refrigerator compartment 2, the ice making room 3 attached to the right and left, the upper freezer compartment 4, the lower freezer compartment 5, and the vegetable compartment 6. . 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 refrigerator compartment 2 is divided into left and right parts, and includes a rotary refrigerator compartment door 2a and a door 2b that are opened in a double-split manner. The ice making chamber 3, the upper freezer compartment 4, the lower freezer compartment 5, and the vegetable compartment 6 are respectively provided with a drawer-type door 3a, The door 4a, the door 5a, and the door 6a are provided. Further, the internal material of the 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 refrigerator compartment 2 is larger than the height H2 of the freezer compartment 7 (H1> H2). In addition, when the distance from the floor to the lower end of the door 2a and 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, so that H5 = 950 mm. , H6 = 1820 mm. As a result, the refrigerator can be used while the user is standing, which improves usability.

  The freezer room 7 is basically a storage room in which the inside of the refrigerator is in the freezing temperature zone (less than 0 ° C.), for example, about −18 ° C., and the refrigerator compartment 2 and the vegetable compartment 6 are in the refrigerator temperature zone ( 0 ° C. or higher), for example, the refrigerator compartment 2 is an average of about 4 ° C. and the vegetable compartment 6 is an average of about 7 ° C. Of the storage rooms, the freezing room 7 is arranged between the freezer room 2 and the vegetable room 6 so that the area of the heat insulating wall separating the freezing room 7 and the outside of the storage room can be minimized. The heat intrusion amount of the refrigerator 1 is reduced to improve the energy saving performance of the refrigerator 1.

  2 is a cross-sectional view taken along the line AA in FIG. 1, and FIG. 3 is a cross-sectional view taken along the line BB in FIG. As shown in the figure, the outside of the refrigerator 1 and the inside of the refrigerator 1 are separated by a box 10 formed by filling a foam heat insulating material (for example, urethane foam) between the outer box 10a and the inner box 10b. Yes. In addition to the foam heat insulating material, a plurality of vacuum heat insulating materials 11 (dotted lines in FIG. 3) are mounted on the box 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 includes a metal layer (for example, aluminum) in order to ensure gas barrier properties, heat is easily transmitted to the outer peripheral side of the vacuum heat insulating material 11 due to the heat conduction of the outer packaging material.

  The refrigerator compartment 2, the upper freezer compartment 4 and the ice making room 3 are separated by a heat insulating partition wall 12a. Similarly, the lower freezer compartment 5 and the vegetable compartment 6 are separated by a heat insulating partition wall 12b. In addition, a heat insulating partition wall 12c is provided 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 so that air inside and outside the chamber does not flow through the gaps of the doors 3a, 4a, and 5a. Is provided. A plurality of door pockets 13 and a plurality of shelves 14 a, 14 b, 14 c, 14 d are provided on the inner side of the doors 2 a, 2 b of the refrigerator compartment 2, and are partitioned into a plurality of storage spaces. The plurality of shelves 14a, 14b, 14c, and 14d are supported by a plurality of support portions (not shown) provided in the inner box 10b on both side surfaces. Since the shelves 14a, 14b, and 14c are provided with support portions at different heights, the installation height of the shelves 14a, 14b, and 14c can be adjusted according to the contents to be stored.

  The freezer compartment 7 and the vegetable compartment 6 are each provided with an ice making container (not shown), an upper freezer compartment container 4b, a lower freezer compartment container 5b, and a vegetable compartment container 6b that are pulled out integrally with the doors 3a, 4a, 5a, 6a. ing.

  Above the heat insulating partition wall 12a, a chilled chamber 15 set lower than the temperature zone of the refrigerator compartment 2 is provided. The chilled chamber 15 has a refrigeration 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, the mode can be switched to about −3 to 0 ° C.

  The evaporator 105 a is a cross fin tube heat exchanger for the refrigerator compartment 2 and is provided in an evaporator chamber 16 a provided on the back side of the refrigerator compartment 2. The air that has become a low temperature by exchanging heat with the evaporator 105a is cooled by a blower 112a provided at a position higher than the evaporator 105a through the casing 17, the discharge air passage 18a, and the discharge port 19a opened upward. 2 cools the inside of the refrigerator compartment 2. The air blown into the refrigerator compartment 2 returns to the evaporator 105a from the return port 20a.

  Here, the form of the blower 112a is a turbo fan. In addition, an opening 21 is provided in the lower part of the casing 17. Thereby, it is suppressed that the dew condensation water which flowed from the discharge air path 18a accumulates, and the malfunctioning of the air blower 112a is prevented.

  The frost grown on the air-side surface of the evaporator 105a can be defrosted without using a heating source such as a heater by operating the blower 112a without flowing a refrigerant through the evaporator 105a. Moreover, since the air blown into the refrigerator compartment 2 at the time of the defrosting operation of the evaporator 105a is around 0 ° C. (frost temperature), the refrigerator compartment 2 can be cooled simultaneously with the defrosting. Therefore, since the form of a present Example has low power consumption compared with the general defrost using heating sources, such as a heater, and can cool the refrigerator compartment 2 without driving a compressor at the time of defrost operation, Even when the defrosting operation is frequently performed, the energy saving performance of the refrigerator 1 is hardly impaired.

  A heater 24a is provided on the surface of the eaves 23a below the evaporator 105a. By energizing the heater 24a, the ice can be melted and drained even if the water accumulated in the basket 23a is frozen. The molten water generated in the jar 23a is discharged to the evaporating dish 26 provided on the upper portion of the compressor 100 through the drain pipe 25a.

  The evaporator 105 b is a cross fin tube heat exchanger for the freezer compartment 7 and is provided in an evaporator chamber 16 b provided on the back side of the freezer compartment 7. The air that has become low temperature by exchanging heat with the evaporator 105b is blown to the freezer compartment 7 through the discharge air passage 18b and the discharge port 19b by the blower 112b provided above the evaporator 105b, and passes through the inside of the freezer compartment 7. Cooling. The air blown into the freezer compartment 7 passes through the freezer compartment return port 20b below the evaporator chamber 105b and returns to the evaporator 105b. Moreover, the propeller fan is used for the form of the air blower 112b.

  In the refrigerator 1 of the present embodiment, the vegetable compartment 6 is also cooled by directly blowing air that has been cooled by the evaporator 105b. The air in the evaporator chamber 16b, which has become low temperature 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). Cool inside. When the vegetable compartment 6 is cold, cooling of the vegetable compartment 6 is suppressed by closing the vegetable compartment damper. The air blown into the vegetable compartment 6 returns to the evaporator chamber 16b through the return air passage 22 from a return port 20c provided in front of the lower part of the heat insulating partition wall 12b.

  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 the deterioration of the cooling performance of the evaporator 105b can be suppressed. The molten water generated during the defrosting falls to a bowl 23b provided at the lower part of the evaporator chamber 16b and is discharged to the evaporating dish 26 provided at the upper part of the compressor 100 in the machine chamber 114 through 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 control of the refrigeration cycle and the blower system is performed according to the control means stored in the control board 29.

  FIG. 4 is a configuration diagram of the refrigeration cycle of the refrigerator according to the first embodiment. The refrigerator 1 according to the present embodiment includes a compressor 100 that compresses refrigerant, an external radiator 101 that is a heat radiating unit, a side heat radiating pipe 102, a front heat radiating pipe 103, capillary tubes 104a and 104b that depressurize the refrigerant, and a heat absorbing means. Evaporators 105a and 105b, gas-liquid separators 106a and 106b that prevent liquid refrigerant from flowing into the compressor 100, a three-way valve 107 that controls the refrigerant flow path, a check valve 108 that prevents reverse flow of the refrigerant, and a refrigeration cycle A dryer 109 that removes moisture therein and a refrigerant junction 110 that connects the refrigerant flow paths are provided, and these are connected by a refrigerant pipe 111 to circulate the refrigerant to constitute a refrigeration 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 refrigerator compartment 2 and the freezer compartment 7. Similarly, the external radiator 101 promotes heat dissipation of the refrigerator 1 by flowing air with the blower 113.

  The refrigerant discharged from the compressor 100 flows in the order of the external heat 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 107b.

  In the refrigeration mode in which the refrigerant flows through 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 junction 110, and then returns to the compressor 100. The refrigerant having a low pressure and low temperature in the capillary tube 104a flows through the evaporator 105a, and the evaporator 105a and the air in the refrigerator compartment 2 exchange heat to cool the items stored in the refrigerator compartment 2.

  In the refrigeration mode in which the refrigerant flows through 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 junction 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 joining portion 110 to the gas-liquid separator 106b side. The refrigerant that has become low pressure and low temperature in the capillary tube 104b flows through the evaporator 105b, and the evaporator 105b and the air in the freezer compartment exchange heat to cool the items stored in the freezer compartment 7.

  FIG. 5 is an arrangement of the heat dissipating means of the refrigerator according to the first embodiment. The external radiator 101 (not shown) is a fin-tube heat exchanger disposed in the machine room 114, the side heat radiation pipe 102 is a heat radiation pipe disposed along the side wall surface of the refrigerator 1, and the front heat radiation pipe 103 is It is the heat radiating pipe arrange | positioned inside the front edge of the heat insulation partition walls 12a, 12b, 12c (refer FIG. 2) of the refrigerator 1. FIG. Further, the side heat radiation pipe 102 is embedded on the outer box 10 a side in the box 10 of the refrigerator 1. The front heat radiation 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 room. Further, the front heat radiation pipe 103 not only radiates heat but also has a role of preventing condensation on the heat insulating partition walls 12a, 12b, and 12c.

  FIG. 6 is a configuration diagram of the evaporator of the refrigerator according to the first embodiment. FIG. 6A is a configuration diagram of the refrigeration evaporator, and FIG. 6B is a configuration diagram of the refrigeration evaporator. As shown in FIG. 6, the evaporator 105a and the evaporator 105b are cross fin tube 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. In the present 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 satisfy Pf1 ≦ Pf2, and further, the height H3 of the evaporator 105a and the evaporation The relationship between the height H4 of the evaporator 105b is configured to satisfy H3 ≦ H4, and the relationship between the width W1 of the evaporator 105a and the width W2 of the evaporator 105b is configured to satisfy W1 ≦ W2. Thereby, the evaporator 105b can suppress the obstruction | occlusion of the flow of the air side by frost growth, ensuring the heat-transfer area, and has improved the energy saving performance of the refrigerator 1 by reducing the energization frequency of the heater 24b. On the other hand, since the evaporator 105a that can be defrosted without using a heater can be reduced in size while ensuring a heat transfer area, the internal volume of the refrigerator compartment 2 is increased without impairing energy saving performance.

  In this embodiment, Pf1 is set to 3 mm and Pf2 is set to 5 mm. However, similar effects can be obtained even if dimensions other than those used in the present embodiment are established if Pf1 ≦ Pf2.

FIG. 7 is a perspective view of the freezer compartment blower according to the first embodiment. In this embodiment, the number of blades of the blower 112b is 3, and the blade diameter is 110mm. In a normal state where there is little food in the cabinet and the frost growth of the evaporator 106b is small, the fan 112b is operated at a rotational speed of about 1100 to 1600min- ^1. ing. By operating the blower 112b, air is blown in the axial direction from the suction side of the fan toward the blowout side.

  As shown in FIG. 2, the freezer compartment 7 has a shorter vertical distance than the refrigerator compartment 2 (H1> H2), and the evaporator 105b provided in the refrigerator compartment 7 has an up-down direction compared to the evaporator 105a provided in the refrigerator compartment 2. 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 freezer compartment 7. In such a front blow-off 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-out direction as the fan mounting form. The air volume can be increased by reducing the air path resistance.

  Further, by using a propeller fan having a wide blade pitch (small number of blades) as in the present embodiment, the fan 112b can always be used in the minus temperature zone as in the freezer compartment 7. The malfunction of the refrigerator 1 generated by frost growth is less likely to occur.

  In the present embodiment, the blower 112a is mounted in the uppermost storage room (refrigeration room). . Generally, a propeller fan is used in a refrigerator as shown in the patent literature. Propeller fans have the characteristic that noise and audibility change easily when the wind path resistance fluctuates. Therefore, the blower 112a which becomes a sound source close to the height of the user's (standing position) ear in front of the refrigerator may give the user an unpleasant feeling. In order to solve the above-described problem, the embodiment 112a is a turbo fan in the present embodiment, and the reason will be described with reference to FIGS.

  FIG. 8A is a cross-sectional view showing a flow form of the propeller fan when the air path resistance is small, and FIG. 8B is a cross-sectional view showing a flow form of the propeller fan when the air path resistance is large. In this embodiment, since the air passage is independent in the refrigerator compartment 2, since the air passage distance is short, the resistance is easily reduced. Therefore, in a normal state where there is little food in the cabinet and there is little frost growth in the evaporator, the air path resistance is relatively small, and the propeller fan flow is often an axial flow as shown in FIG. . On the other hand, in a high load state where there is a lot of food in the cabinet 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 be centrifugal as shown in FIG. 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, in a normal state where there is little food in the cabinet and frost growth in the evaporator is small, the air volume is relatively large and the noise level is small. On the other hand, in a high load state where there is a lot of food in the cabinet and there is a lot of frost growth in the evaporator, the air volume is relatively small and the noise level is large.

  From 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 hearing.

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

  Turbofans have characteristics that make it easier to increase airflow at high static pressure (high airflow resistance) compared to propeller fans, in other words, low airflow and noise increase at high static pressure. . In addition, since the flow form does not change significantly due to fluctuations in the operating air volume, the change in audibility is small depending on the operating air volume.

  Therefore, even when the resistance is increased due to the food being put into the refrigerator compartment 2 and the air passage is narrowed, or when the resistance is increased due to the growth of frost in the evaporator 105a, the noise of the blower 112a is increased and the audibility is changed. Even if the blower 112a is provided at a position close to the height of the ear of the user (standing position) in front of the refrigerator (door side), it is possible to make it difficult for the user to feel uncomfortable. .

  In the present embodiment, the blower 112a is a turbo fan. However, even when a sirocco fan is used, the flow form is difficult to change when the operating point fluctuates, and thus a change in audibility can be suppressed similarly to the turbo fan. On the other hand, when attention is paid to the absolute value of noise generated from the fan, the turbo fan is smaller.

  11A is a cross-sectional view of a sirocco fan, and FIG. 11B is a cross-sectional view of a turbo fan. As shown in FIG. 11A, the sirocco fan has blades arranged in a forward direction with respect to the flow direction. Due to the characteristics of the blades, since the direction of flow is small, the blown wind speed is higher than that of the turbofan, and noise is likely to increase (same rotation speed, same fan diameter comparison). On the other hand, as shown in FIG. 11 (b), the turbofan has blades arranged rearward with respect to the direction of the blowing flow. Due to the characteristics of the blades described above, since the direction of flow is large, the blown wind speed is lower than that of a sirocco fan, and noise tends to be small. Therefore, by setting the form of the blower 112a as a turbo fan, even when a change in audibility due to fluctuations in the wind path resistance occurs, the user is less likely to notice and can be made more uncomfortable to the user. .

  FIG. 12 is a graph showing the relationship between the noise transmittance and the area density of the door. The absolute value of the noise can be further reduced by optimizing the area density of the door as well as the shape of the blower 112a. The transmitted sound Lt that can be heard through the door can be obtained by equations (1) to (2).

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

  In the figure, the incident sound (sound source) is 20 dB, the typical noise frequency 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 door area density. It is the result represented by. The representative frequency of the noise is the peak frequency of the fan alone at the maximum rotational speed of the blower 112a, which is a noise level that is likely to cause discomfort to the user. In this embodiment, the door is a urethane single phase, but in the case of multiple layers, the value of each layer is the total value. Specifically, in the case where a steel sheet or a resin material is provided on the surface of urethane, the calculation is performed in consideration of these.

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

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

  In the present embodiment, the two blowers 112a and 112b have different forms. Thereby, since the peak frequency band of noise caused by the number of fan blades and the number of rotations can be greatly shifted, it is possible to prevent a sudden increase in noise generated from the refrigerating room 2 and a deterioration in hearing.

In this embodiment, the noise (Z1 × N1) caused by the number of turbofan blades Z1 and the operating rotational speed N1 is generated at 183 to 267 s ⁻¹ , and the noise caused by the propeller fan blade count Z2 and the operating rotational speed N2 (Z2 × N2) is generated at a frequency of 55 to 80 s ⁻¹ . Therefore, since the relationship of N1 × Z1 ≠ N2 × Z2 in which these two peak frequency bands are different holds, not only the reduction of fluid sounds distributed in a wide frequency band but also a rapid increase in noise in the peak frequency band can be prevented. Thereby, even if it is a case where a change arises in a noise characteristic (audibility), it becomes difficult for a user to notice.

Moreover, the noise of a multiple of NZ sound (2NZ sound) is next 367～533S ^-1 turbofan, a 110～160S ^-1 propeller fan. Therefore, even when the 2NZ sound generation range is included in addition to the 1NZ sound, since the peak frequency bands generated from the two fans 112a and 112b are different, it is possible to prevent a rapid increase in noise. In the present embodiment, the frequency bands of the turbofan and the propeller fan are compared using an average value over a predetermined time during normal operation, and do not prevent the peak frequency bands from being instantaneously matched. Absent.

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
The noise that can be heard through the doors of the refrigerator compartment 2 (door 2a, door 2b) is higher than the noise that can be heard through the doors of the freezer compartment (door 3a, door 4a, door 5a). Can be small. The reason for this will be described with reference to FIG.

FIG. 13 is a graph showing the relationship between noise transmittance and frequency. The figure shows the calculation result when the incident sound (sound source) is 20 dB. The vertical axis represents the ratio of the transmitted sound Lt to the incident sound Li (transmittance = Lt / Li × 100%), and the horizontal axis represents the frequency. . From the figure, the transmittance of the propeller fan in the 1NZ range is about 100%, whereas the transmittance of the turbofan in the 1NZ range is 49 to 66%. Therefore, a refrigerator with low noise in the peak frequency band generated from the refrigerator compartment 2 can be provided by selecting a turbo fan as the form of the blower 112a of the refrigerator compartment 2. Here, in this embodiment, the thickness of the door (door 2a, door 2b) of the refrigerator compartment 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 turbo fan as the form of the blower 112a of the refrigerator compartment 2, it is possible to provide a refrigerator with a small change in audibility generated from the refrigerator compartment 2 and low fluid noise.

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

  14A is a cross-sectional view showing a comparative example when one propeller fan is mounted vertically, FIG. 14B is a cross-sectional view showing a comparative example when one propeller fan is mounted horizontally, FIG. (C) is sectional drawing which shows the comparative example at the time of mounting one small diameter propeller fan horizontally.

  As shown in FIGS. 14A to 14C, 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, a space for turning the flow direction is 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 is larger than the depth dimension 31 of the evaporator 105a, and the internal volume of the refrigerator compartment 2 is likely to decrease.

  In the form in which the propeller fan is arranged substantially horizontally as the blower 112a as shown in FIG. 14B, there is no obstacle to the flow direction, so that it can operate without impairing the blowing efficiency. The depth dimension 30 needs to be equivalent to the diameter of the blower 112a. Therefore, the depth dimension 30 of the air passage around the blower 112a is larger than the depth dimension 31 of the evaporator 105a, and the internal volume of the refrigerator compartment 2 is likely 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 reduced. Therefore, in the form of FIG. 14C, when a plurality of propeller fans (for example, two) are arranged in parallel in the left-right direction of the refrigerator 1 as the blower 112 a and are arranged substantially horizontally, the depth dimension of the blower passage around the blower 112 a. 30 can be brought close to the depth dimension 31 of the evaporator 105a to ensure a sufficient air volume. However, since the blowers 112a are arranged in parallel, when the 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 be deteriorated. 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. 14B and 14C. The solid line shows the configuration shown in FIG. 14 (b), the dotted line shows the configuration shown in FIG. 14 (c) and one propeller fan, and the alternate long and short dash line shows the configuration shown in FIG. 14 (c) when two propeller fans are arranged in parallel. Is shown. Further, here, in order to facilitate understanding of the characteristics, the cases where the rotation speeds of the fans are the same are shown, and the respective operating points are indicated by black circles.

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

  As shown in FIG. 15 (b), when frost grows on the surface of the evaporator, it becomes a condition of high static pressure and low air volume, so the resistance curve is steep as shown in the figure. Therefore, with respect to the form of FIG. 14B, the form of FIG. 14C (two propeller fans) reduces the air volume, and the energy saving performance of the refrigerator 1 is lowered.

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

  FIG. 16 is a diagram showing the relationship between the aerodynamic characteristics and resistance curves of a propeller fan and a turbo fan having the same blade diameter and the same rotation speed. As shown to Fig.16 (a), in the normal state with few frost adhesion to the evaporator 105a, when a turbo fan is mounted and the case where a propeller fan is mounted, an equivalent air volume can be ensured. As shown in FIG. 16 (b), in the state where frost has grown on the surface of the evaporator 105a, by installing the turbo fan as in this embodiment, the air volume can be increased as compared with the case where the propeller fan is mounted. Can do. In the present embodiment, as described above, since the blower 112a is operated even when the evaporator 105a is defrosted, the energy saving performance of the refrigerator 1 can be improved by improving the efficiency of the defrosting operation.

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

  Thus, according to the present Example, the propeller fan is selected as the form of the fan 112b of the freezer compartment 7 and the turbo fan is selected as the form of the fan 112a of the refrigerator compartment 2, thereby increasing the internal volume of the refrigerator 1 and increasing. Both energy saving performance can be achieved.

  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 the present embodiment, a turbo fan is arranged substantially vertically as the blower 112a. Moreover, the front side edge part of the air blower 112a is located in the back side rather than the front side edge part of the evaporator 105a. The vertical projection of the blower 112a and the vertical projection of the evaporator 105a are at least partially overlapped. In this embodiment, the vertical projection of the blower 112a is included in the vertical projection of the evaporator 105a. .

In this embodiment, the number of turbofan blades is 10 and the blade diameter is 100 mm. During normal operation, the blades are operated at a rotational speed of about 1100 to 1600 min- ¹ . Since the turbo fan 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. Thereby, since the depth dimension 30 of the air flow path of the part (blower 112a periphery) which has arrange | positioned the air blower 112a can be made equivalent to the depth dimension 31 of the evaporator 105a without impairing air blowing efficiency, it contributes to the increase in an internal volume. can do. Here, “equivalent” means that the distance from the rear side of the partition 40 facing the front side to the blower 112a to the front side of the inner box 10b (depth dimension 30 of the blower passage around the blower 112a) is the evaporator. The depth dimension 31 of 105a is within ± 20%, preferably within ± 10%. When the partition 40 is not straight in the vertical direction, the depth dimension 30 of the air passage 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 refrigerator compartment 2 is configured to be lower. Therefore, when the fan is stopped, air flows from the upper side to the lower side due to natural convection, so that the cold air in the minus temperature zone around the evaporator 105a hardly flows through the blower 112a and the casing 17, and the dew condensation adhered to the turbo fan and the casing. Phenomenon such as water freezing, frost formation and frost growth hardly occurs. Therefore, even when the fan is moved again, malfunctions due to frost formation and freezing are less likely to occur. Furthermore, since the frost that has grown upward in the evaporator 105a is blocked by the casing 17, malfunction caused by contact of the frost with the blower 112a is less likely to occur.

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

  The communication flow path 33 extending from the opening 21 to the evaporator chamber 16a is provided with a turning wall 21a (air path resistance adding means) for increasing the air path 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 inlet 17b and pressurized by the blower 112a does not go to the discharge air passage 18a but flows from the opening portion 21 to the evaporator chamber 16a through the communication passage 33, and again to the inlet. Returning to 17b, the pressure is increased (flow indicated by a dotted line in FIG. 17). Due to this flow, the amount of air circulating through the refrigerator compartment 2 is reduced, and the energy saving performance is lowered.

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

  In addition, a part of the turning wall 21a is provided on the front side of the communication flow path 33, which serves as a directional flow path that prevents discharge toward the inflow port 17b. As a result, the resistance until the air discharged into the evaporator chamber 16a reaches the inlet 17b is increased, and it is difficult for the air to be sucked into the inlet 17b. Therefore, the amount of air discharged through the opening 21 is reduced, thereby saving energy. A decrease in performance can be suppressed.

  18 is a cross-sectional view taken along the line CC of FIG. The blower 112 a is provided in the casing 17. When the blower 112a is rotated clockwise (in the direction of the solid line arrow in FIG. 18), the air flows toward the discharge air passage 18a as indicated by the dotted line arrow in FIG. 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 discharges while being directed rightward in FIG. 18 by the turning wall 21a. As a result, the air discharged from the opening 21 is discharged by turning the direction of the circumferential flow formed in the rotation direction of the blower 112a by approximately 180 degrees, so that the air path resistance of the communication flow path 33 is increased and the opening is opened. By reducing the air flow leaking from the portion 21, it is possible to suppress a decrease in energy saving performance.

  Moreover, as shown in FIG. 18, the casing 17 is provided with a tongue portion 17c serving as a starting point of the spiral enlarged flow path at the lower end of the side wall on the blower 112a side of the discharge air passage 18a. When the width of the fan blade is Lf and the width from the tongue portion 17c to the right end of the casing 17 across the fan is Lk, Lf is configured to be within the range of Lk. This prevents the condensed water generated in the discharge air passage 18a and the discharge port 19a (described in FIG. 2) from adhering to the wings 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 becomes a highly reliable refrigerator in which the air blowing performance is reduced due to icing between the blades and abnormal noise is not generated due to the contact of the grown ice with the casing 17.

  Further, the minimum width 60 of the communication flow path 33 extending from the opening 21 to the evaporator chamber 16a (approximately approximately in this embodiment) than the average stacking interval Pf1 of the fins of the evaporator 105a (3 mm in the present embodiment, described in FIG. 6). 6 mm) and the minimum width 61 (about 6 mm in the present embodiment) between the blades of the blower 112 a are configured to be large. By configuring the refrigerator compartment 2 with the dimensional relationship as described above, when the frost grows, the fins of the evaporator 105a are most likely to be blocked. Therefore, by performing the defrosting operation so as to avoid the blockage between the fins of the evaporator 105a, the communication channel 33 having a relatively large width and the blockage between the blades are hardly generated, and the refrigerator has high reliability.

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

When the refrigerator compartment 2 is cooled by the refrigerator operation and the refrigerator compartment temperature decreases to T _Roff (time t ₁ ), the refrigerator 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. Thereby, the refrigerant shortage in the next freezing operation is suppressed. At this time, the blower 112a is driven so that the residual refrigerant in the evaporator 105a can be used for cooling the refrigerator compartment 2, and the refrigerant in the evaporator 105a evaporates and easily reaches the compressor 100. Therefore, the cooling efficiency can be increased by collecting a large amount of refrigerant in a relatively short time.

When the refrigerant recovery operation ends (time t ₂ ), the operation is switched to the freezing operation for cooling the freezer compartment 7. In the refrigeration operation, the three-way valve 107 is set to the outlet 107b side, the refrigerant is flowed to the evaporator 105b, and the evaporator 105b is cooled. By operating the blower 112b in this state, the freezer compartment 7 is cooled by the air that has passed through the evaporator 105b and has become low temperature. This freezing operation is performed until the freezer temperature reaches T _Foff (time t ₅ ). During the freezing operation, the vegetable compartment damper (not shown) is also opened, and the vegetable compartment 6 is cooled until the vegetable compartment temperature becomes T _Roff (time t ₃ ).

  Furthermore, in the refrigerator 1 of the present embodiment, the defrosting operation of the evaporator 105a is performed during the 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 evaporator 105a during the freezing operation, when the air in the refrigerator compartment 2 passes through the evaporator 105a, the evaporator 105a is exchanged with the refrigerator compartment 2 having a higher temperature than the evaporator 105a. And the frost adhering to the evaporator 105a is heated. The defrosting of the evaporator 105a is performed by this heating. In addition, since air is cooled by the frost adhering to the evaporator 105a and the evaporator 105a, and this air is ventilated by the air blower 112a to the refrigerator compartment 2, the refrigerator compartment 2 can be cooled. Therefore, frost adhering to the evaporator 105a can be melted without using a heater, and in addition, the refrigerator compartment 2 can be cooled. Therefore, the defrosting operation of the evaporator 105a of the present embodiment has high energy saving performance. It is frost operation.

Further, by this defrosting operation, in addition to the evaporator 105a, 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 ).

If none of the defrosting operation and the freezing operation of the evaporator 105a termination condition is satisfied (time t _5), performs a refrigerant recovering operation to again drive the compressor 100 to the three-way valve 107 in a fully closed state, in the evaporator 105b Recover the refrigerant and suppress the shortage of refrigerant in the next refrigeration operation. At this time, the blower 112b is driven, so that the residual refrigerant in the evaporator 105b can be used for cooling the freezing 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 increased.

At time t ₆ when the return to the refrigerating operation to repeat the operation described above. The above is the basic cooling operation of the refrigerator of this embodiment and the defrosting control of the evaporator 105a. By these operations, the refrigeration room 2, the freezing room 7, and the vegetable room 6 are cooled and maintained at a predetermined temperature, and the frost growth of the evaporator 105a is suppressed.

Before the end condition of the defrosting operation of the evaporator 105a (temperature of the evaporator 105a is T _DR) is satisfied, if it meets the termination condition of the freezing operation (freezing compartment temperature is T _Foff) is The compressor 100 is turned off while continuing the defrosting operation of the evaporator 105a. Then, if the completion | finish conditions of the defrost operation of the evaporator 105a are satisfy | filled, the compressor 100 will be turned ON and it will transfer to refrigeration operation. Thereby, it is suppressed that the frost and defrost water adhering to the evaporator 105a in the middle of melting | fusing, the casing 17, and the air blower 112a are cooled again by refrigerating operation, and refreeze.

Further, the freezing compartment temperature at time t ₁ and time t ₂ is lower than a predetermined value, also refrigerating compartment temperature at time t ₅ and time t ₆ is stopped even compressor 100 is lower than a predetermined value. Thereby, the excessive cooling in a store | warehouse | chamber can be suppressed.

  In the refrigerator of this embodiment controlled as described above, the defrosting operation time (time t1 to t4 in the figure) of the refrigerator compartment is longer than the refrigeration operation time (time t0 to t1 in the figure). . Thereby, in the air around the casing 17 and the blower 112a, the time during which the temperature rises can be made longer than the time during which the temperature falls, so that the casing 17 and the blower 112a can be sufficiently heated without using a heater, and energy saving performance is high. Become a refrigerator.

  Moreover, in the refrigerator of a present Example, the air around casing 17 and the air blower 112a is comprised so that the time when it becomes plus temperature may become longer than the time when it becomes minus temperature.

  In addition, in the refrigerator of the present embodiment, in the driving state of the compressor 100, the time for which the refrigerant flows to the outlet 107b of the three-way valve is set longer than the time for the refrigerant to flow to the outlet 107a of the three-way valve. Thereby, the time for which the evaporator 105a is constant in the plus temperature zone or the temperature rise can be made longer than the time for the evaporator 105a to be constant in the minus temperature zone or to decrease in temperature. Accordingly, the temperature around the casing 17 and the blower 112a can be longer during the time of the plus temperature than the time of the minus temperature. For this reason, 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 operation time of the blower 112a is configured to be longer than the stop time. Thereby, 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. However, the control is based on the time so as to end when the defrosting operation is continued for a predetermined time. Thus, the defrosting operation time of the refrigerating room may be longer than the refrigerating operation time. Further, in the refrigerator of the present embodiment, when the average temperature of the constituent elements in the periodic control is evaluated, it is sufficient that the above-mentioned characteristics are provided, even when the characteristics differ locally or in the short term. Similar effects can be obtained.

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

  Moreover, since the outer box 10a which is the upper surface is in contact with outside air and the heat insulating partition wall 12a which is the lower surface of the refrigerator compartment 2 is in contact with the freezer compartment, the upper surface side of the refrigerator compartment 2 of the present embodiment is most easily warmed. It has a configuration. Therefore, the casing 17 is provided with the discharge port 19a and opens upward, so that the region most easily warmed can be efficiently cooled. Furthermore, when the blower 112a is stopped, the low temperature air in the upper part of the refrigerator compartment 2 flows downward, so that the food in the refrigerator can be efficiently cooled.

  Furthermore, in this embodiment, since the blower 112a is a turbo fan, even when frost grows on the surface of the evaporator 105a, low-temperature air can be supplied into the refrigerator compartment 2 by a large air volume, Suitable for soaking. Moreover, the evaporator 105a is for the refrigerator compartment 2, and since the temperature is higher than the evaporator 105b for the freezer compartment 7, air in a state close to the refrigerator temperature zone can be supplied into the refrigerator compartment 2, so that temperature adjustment is possible. There is an advantage that it is easy to do. As a result, according to the present embodiment, the average temperature of the entire refrigerating chamber 2 can be kept at 3 ° C. or lower, preferably about 2 ° C. lower than the conventional temperature, and the effect of maintaining the freshness in the refrigerating chamber 2 is enhanced.

  As shown in FIG. 20, the discharge air passage 18 a 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. In general, when the blower 112 a is provided with the spiral casing 17, the blower 112 a tends to contract toward the outer peripheral side of the casing 17. Therefore, since it becomes easy for the wind to flow to the left side of the discharge air passage 18a, if a discharge air passage extending linearly upward is formed, the discharge air is shifted to the left side, and the right side of the refrigerator compartment 2 is difficult to cool. Therefore, as shown in the present embodiment, the discharge air passage 18a is configured with a curved surface that faces the right side as a whole, thereby deflecting the wind direction to the right side and making the refrigerator compartment 2 uniform temperature. Due to these uniform temperature effects, the refrigerator compartment 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, by providing a heat insulating material 52 around the discharge air passage 18 a and the casing 17, condensation in the refrigerator compartment 2 is prevented. Moreover, the heat insulating material 52 is covered with the decorative cover 53 (a side view is described in FIG. 2), and the decorative cover 53 is a substantially vertical surface. By providing such a decorative cover 53, when the installation position of the shelves 14a, 14b, 14c is changed in the vertical direction, a gap is formed between the shelf and the decorative cover 53, and food or the like falls from the gap. It becomes a convenient refrigerator that has no. Further, in the present embodiment, the heat insulating material 52 is provided around the discharge air passage 18a and the casing 17. However, even when the heat insulating material is partially reduced to be hollow, condensation in the refrigerator compartment 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 so that the wind speed is faster because the air passage is narrower than the refrigerator compartment 2 and the evaporator compartment 16a. . Among them, the wind speed around the blower 112a is particularly fast because the air flowing out from the evaporator 105a joins, and the box 10 near the blower 112a is likely to infiltrate heat. On the other hand, since the side heat radiation pipes 102 are provided on the left and right sides of the box body 10, the surface of the inner box 10 b on both the left and right side surfaces is more easily intruded from the center side.

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

  Further, in this embodiment, since the vacuum heat insulating material 11 is provided on the back side of the box body 10, the outer peripheral side of the back side of the box body 10 is configured to easily infiltrate compared to the center side. By disposing the blower 112a substantially at the center in the left-right direction of the refrigerating chamber 2, the wind speed can be lowered at a location where heat can easily enter in the box 10, so that the heat intrusion amount of 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 disposed so as to pass through a part of the blower 112a. Thereby, since the nonuniformity of the wind speed distribution of the evaporator 105a can be minimized, the energy saving performance of the refrigerator 1 can be improved.

  FIG. 21 is an enlarged view of the main part of FIG. 2 showing the relationship between the shelf of the refrigerator compartment and the air passage according to the present embodiment. In the present embodiment, the food storage space in the refrigerator compartment 2 is expanded by optimizing the relationship between the arrangement of the air channel and the shelf provided with the turbofan. As shown in the figure, the refrigerator 1 according to the present embodiment includes a partition 40 between the refrigerator compartment 2 and the evaporator chamber 16a, and the upper surface 41 of the partition and the upper surface of the shelf 14c are substantially horizontal, and the height of each other is substantially the same. They are arranged to match. Thereby, since the upper surface 41 of a partition can be utilized as extension of the shelf 14c, it becomes possible to increase food storage space.

  In this embodiment, in order to increase the space efficiency, the upper surface 41 of the partition and the upper surface of the shelf 14c are brought into contact with each other, but there may be a slight gap without making contact. Further, the partition 40 is configured substantially vertically. 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. Improved usability. In the present embodiment, the entire area of the partition 40 is substantially vertical, but the same effect can be obtained with 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 doors). The figure shows a structure excluding doors 2a and 2b in order to visualize the internal structure. A chilled chamber 15 is provided at the lower right of the refrigerator compartment 2, a water storage tank 70 for ice making is provided at the lower left of the refrigerator compartment, 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, and in this embodiment, the first return port 72a is on the left side between the shelf 14c and the shelf 14d, and the first return port 72a is on the right side between the shelf 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. Thus, by providing the air return port 20a between the shelves 14c and 14d, the amount of air flow flowing around the partition 12a between the refrigerator compartment 2 and the freezer compartment 7 is reduced. By this. The amount of heat exchanged by forced convection between the refrigerator compartment 2 and the freezer compartment 7 is reduced, and as a result, the time for the freezing operation in which the compressor is operated at a relatively high speed is reduced, so that the energy saving performance of the refrigerator can be improved.

In this embodiment, the main flow of air for cooling the refrigerator compartment 2 is the first return ports 72a and 72b.
The airway is configured to flow through Thereby, since the air path resistance of the first return ports 72c and 72d becomes relatively large, it becomes difficult for air to flow, so that the amount of heat exchanged by forced convection between the refrigerator compartment 2 and the freezer compartment 7 can be further reduced.

  In addition, it is measured in the state which obstruct | occluded the 1st return ports 72c and 72d that the air flow is comprised so that the main flow of the air which cools the refrigerator compartment 2 may flow through the 1st return ports 72a and 72b. This can be determined by comparing the upper surface temperature of the partition 12a with the temperature at the same position of the partition 12a measured with the first return ports 72c and 72d opened. Specifically, during normal operation, the time average value of the upper surface temperature of the partition 12a measured with the first return ports 72c and 72d closed, and the first return ports 72c and 72d opened. If the difference in the time average value of the temperature at the same position of the partition 12a measured in (1) is 1 ° C. or less, it can be said that the main flow of air for cooling the refrigerator compartment 2 flows through the first return ports 72a and 72b. In the present embodiment, the sum of the air path cross-sectional areas of the first return ports 72a and 72b is made larger than the sum of the air path cross-sectional areas of the first return ports 72c and 72d. Thereby, since the air path resistance of the first return ports 72c and 72d becomes relatively large, it becomes difficult for the air to flow, so that the amount of heat exchanged by forced convection between the refrigerator compartment 2 and the freezer compartment 7 can be reduced more reliably.

  Furthermore, since a plurality of first return openings are provided between the shelves 14c and 14d and below the shelf 14d, the total opening area can be expanded as compared with the case where one first return opening is provided. By reducing the road resistance, the circulation air volume can be increased and the energy saving performance of the refrigerator compartment 2 can be improved.

  Here, the air passage cross-sectional area of the present embodiment refers to the area in a plane perpendicular to the air flow direction, and the air passage having the smallest area among them. For this reason, 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 with a sealing material or the like.

  In this embodiment, the first return ports 72a and 72b are provided in order to reduce the amount of heat exchanged by forced convection between the refrigerator compartment 2 and the freezer compartment 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 that water in the water storage tank 70 is frozen occurs. In order to solve this problem, in this embodiment, the air passage sectional area of the first return port 72c is made larger than the air passage sectional area of the first return port 72d. Thereby, it is possible to make the water in the water storage tank difficult to freeze while reducing the amount of heat exchanged by forced convection between the refrigerator compartment 2 and the freezer compartment 7.

  23 is a cross-sectional view taken along the line DD of FIG. As shown in the drawing, 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, in order to drain the dew condensation water, the ridge 23a is inclined so that the distance H8 between the right lower end of the evaporator and the ridge is larger than the distance H7 between the lower left end of the evaporator and the ridge. For this reason, the air flowing in from the first return port 72a has a large air path resistance due to the short distance H7 between the left lower end of the evaporator and the eaves, and the air volume may be reduced. Therefore, in this embodiment, since the above problem is solved by providing a plurality of second return air passages, a description will be given with reference to FIG.

  FIG. 24 is a front perspective view of a refrigerating room (without doors, water storage tanks, chilled rooms, and surrounding heat insulating walls). The figure shows the structure excluding the doors 2a and 2b, the water storage tank 70, the chilled chamber 15, and the surrounding heat insulating walls in order 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. As described above, since the opening area can be increased by providing a plurality of second return ports, the air that has passed through the first return port 72a is less likely to contract at the second return ports 73a, 73b, 73c, and is refrigerated. The air volume circulating through the chamber 2 increases, 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 electrical 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. In this way, by arranging the electrical component box 74 on the back side of the water storage tank 70, a space that has a large air passage area and cannot be used for storing food can be effectively used. Space expansion can be achieved at the same time.

  Next, the refrigerator which concerns on Example 2 of this invention is demonstrated using FIG. The second embodiment is different from the first embodiment in the structure of the door (door 2a, door 2b) of the refrigerator compartment 2. Other configurations are the same as those in the first embodiment, and redundant description is omitted.

  26 is a cross-sectional view taken along the line AA in FIG. As shown in the figure, the door 2 a and the door 2 b of the refrigerator compartment 2 are composed of urethane 65 and a vacuum heat insulating material 11. Thus, by inserting a high heat insulation layer in the door 2a and the door 2b, noise can be reduced as compared with the case of urethane alone, and this makes it difficult for the user to notice even when the auditory sensation changes. . Furthermore, since the vacuum heat insulating material 11 has a low thermal conductivity with respect to the urethane 65, the amount of heat entering the refrigerator compartment 2 from the outside air can be reduced, and the energy saving performance of the refrigerator 1 can be improved.

  Next, the refrigerator which concerns on Example 3 of this invention is demonstrated using FIGS. 27-28. The third embodiment is different from the first embodiment in the structure of the door (door 2a, door 2b) of the refrigerator compartment 2. Other configurations are the same as those in the first embodiment, and redundant description is omitted.

27 is a cross-sectional view taken along the line AA in FIG. As shown in the figure, the door 2a and the door 2b of the refrigerator compartment 2 are made of urethane 65, and the surface 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 the refrigerator is 40 to 60 kg / m ³ , and the average density of glass is 2400 to 2600 kg / m ³ . Thus, by providing the glass 66 on the surfaces of the door 2a and the door 2b, the area density can be greatly improved as compared with the case where only the urethane 65 is used. Furthermore, since the surface of the door 2a and the door 2b is made of glass 66, it becomes difficult to be scratched, so that the durability performance can be improved and the appearance performance can also 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 of urethane 65 and glass 66 to the calculation result for the urethane 65 single phase of FIG. From the figure, when 5 mm of glass 66 is added to the surfaces of the doors 2a and 2b, the transmittance in the 1NZ range of the propeller fan is about 13 to 29%, whereas the transmittance in the 1NZ range of the turbofan. The rate is 0%. Therefore, the refrigerator is provided with glass 66 on the surfaces of the door 2a and the door 2b, and the noise in the peak frequency band generated from the refrigerator compartment 2 is eliminated by selecting a turbo fan as the form of the blower 112a of the refrigerator compartment 2. can do.

  In this embodiment, the thickness of the urethane 65 is 40 mm and the thickness of the glass 66 is 5 mm. However, the dimensions are not necessarily described, and the dimensions may be changed if the same effect can be obtained. .

  The above is the form of this embodiment. In addition, this invention is not limited to the form mentioned above, Various modifications are included. For example, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described. In addition, it is possible to add, delete, and replace other configurations for a part of the configuration of the embodiment.

1 Refrigerator 2 Refrigerated room 3 Ice making room 4 Upper freezer room 5 Lower freezer room Freezer room 6 Vegetable room 7 Freezer room (generic name for 3, 4 and 5)
DESCRIPTION OF SYMBOLS 10 Box 10a Outer box 10b Inner box 11 Vacuum heat insulating material 12a, 12b, 12c Thermal insulation partition wall 13 Door pocket 14a, 14b, 14c, 14b Shelf 15 Chilled room 16a, 16b Evaporator room 17 Casing 17a Casing lower surface 17b Casing bottom Inlet 17c Casing tongues 18a, 18b Discharge air passages 19a, 19b Discharge ports 20a, 20b, 20c Return port 21 Opening portion 21a Turning wall (air flow resistance adding means)
22 Return air passages 23a, 23b Reeds 24a, 24b Heaters 25a, 25b Drain pipe 26 Evaporating tray 27 Cover 28 Temperature sensor 29 Control board 30 Depth dimension 31 of the air passage around the blower 112a Depth dimension 32 of the evaporator 105a Dimensions perpendicular to the air flow direction 33 Communication channel 40 Partition 41 Partition upper surface 50 Wind direction plate 52 Heat insulating material 53 Cosmetic cover 60 Minimum width 61 of the communication channel 33 from the opening 21 to the evaporator chamber 16a 61 Blades of the 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 (between shelves, right)
72c 1st return port (around water storage tank)
72d First return (around chilled room)
73a Second return (bottom left)
73b Second return (upper right)
73c Second return (center)
74 Electrical component box 100 Compressor 101 External heat sink 102 Side heat radiation pipe 103 Front heat radiation pipe 104a, 104b Capillary tubes 105a, 105b Evaporators 106a, 106b Gas-liquid separator 107 Three-way valve 108 Check valve 109 Dryer 110 Refrigerant merge section 111 Refrigerant piping 112a, 112b Blower 113 Blower 114 Machine room 115 Fin 116 Heat transfer pipe

Claims (5)

  A refrigerator room, a freezer room, and a vegetable room are arranged from above, and includes a compressor, a heat radiating unit that radiates heat of the refrigerant that has been compressed by the compressor, and a temperature increasing unit, and a pressure reducing unit. An evaporator in which the low-temperature refrigerant exchanges heat with the air in the cabinet, a blower for circulating the cold air generated by the evaporator, and for carrying the air blown by the blower to each storage chamber A refrigerator comprising an air passage, a chilled chamber below the refrigerator compartment, and an outlet and a return port for the air passage above the chilled chamber.   The refrigerator according to claim 1, wherein the main stream flows through a return port above the chilled chamber.   3. The refrigerator according to claim 1, wherein the sum of the opening areas of the return ports is larger than an air passage cross-sectional area around the chilled chamber and around the water storage tank.   4. The refrigerator according to claim 1, wherein an air passage sectional area around the water storage tank is larger than an air passage sectional area around the chilled chamber.   5. The refrigerator according to claim 1, wherein a plurality of openings are provided in a side surface and a front surface in an evaporator chamber for storing the evaporator. 6.

Images