KR20130083871A - Refrigerator and freezer - Google Patents

Abstract

PURPOSE: A refrigerator and a freezer are provided to suppress the inflow of a high-temperature refrigerant from a condenser which becomes a thermal load of an evaporator when compressors stop, thereby obtaining excellent energy saving performance. CONSTITUTION: A refrigerator includes an insulating box body (10) and a freezing cycle (1S). The insulating box body insulates the inside of a storage compartment from the outside thereof. The freezing cycle includes a compressor (24), first condensers (61,62), a second condenser (64), a third condenser (63), a flow passage conversion valve (65), and an decompression member (43) and circulates a refrigerant. The second condenser is arranged in a rim portion of a front opening of the insulating box body. The third condenser is installed at a spot except for the rim portion of the front opening of the insulating box body. The flow passage conversion valve converts flow passages to the second and third condensers. The freezing cycle includes an evaporator and circulates the refrigerant. A cut-off member is installed between the downstream flow passage of the second condenser and the downstream flow passage of the third condenser. A second control unit controls the cut-off member so that the cut-off member stops when the compressor stops.

Description

Refrigerators and Freezers {REFRIGERATOR AND FREEZER}

The present invention relates to a refrigerator and a freezer in which power consumption is reduced.

Conventionally, the following patent document 1 is mentioned as a background art of this technical field.

The refrigerator described in Patent Literature 1 connects a heat insulation box body in which a storage compartment is provided, a compressor, a first condenser, a flow path switching valve, a second condenser provided on the outer surface of the heat insulation box body, a decompression means, and an evaporator. A first refrigeration cycle is provided, and a third condenser provided in addition to the outer surface of the heat insulation box that is switched from the second condenser provided on the outer surface of the heat insulation box by the flow path switching valve.

And the said refrigerator comprises the 2nd refrigeration cycle by using the 3rd condenser provided in addition to the outer surface of the heat insulation box switched from the 2nd condenser by replacing with a 2nd condenser.

Patent Literature 1 discloses a refrigerator that suppresses condensation on the outer surface of the thermal insulation box while suppressing heat intrusion from the second condenser provided on the outer surface of the thermal insulation box by operating while switching the first and second refrigeration cycles. Is disclosed.

Japanese Patent Application Laid-Open No. 2009-275964 (FIGS. 1 to 3, etc.)

However, in the refrigerator described in Patent Document 1, when the compressor is stopped, the high-temperature refrigerants respectively present in the second condenser and the third condenser of the heat dissipation pipe flow into the evaporator responsible for cooling in the furnace, and energy due to the increase in the heat load of the evaporator. It is caused by deterioration of the saving performance.

This invention is made | formed in view of the said subject, and aims at providing the refrigerator and freezer with high energy saving performance by suppressing deterioration of the energy saving performance by the inflow of a high temperature refrigerant | coolant to an evaporator.

In order to achieve the above object, the refrigerator according to the first aspect of the present invention is a heat insulating box that insulates the storage compartment and the outside of the refrigerator, and a compressor, a first condenser, and a second condenser arranged at the front opening edge of the heat insulating box. And a third condenser provided at a place other than the front opening edge of the heat insulating box, a flow path switching valve for switching the flow path to the second condenser and the flow path to the third condenser, a pressure reducing means, and an evaporator. A refrigerator having a refrigeration cycle for circulating, wherein the compressor is operated after closing the flow paths on the second condenser side and the third condenser side for a predetermined time in the flow path switching valve. And a first control unit for controlling the refrigerant recovery to reduce the amount of refrigerant in the second condenser and the third condenser.

The freezer which concerns on 3rd this invention applies the refrigerator which concerns on 1st this invention to a freezer.

The refrigerator which concerns on 2nd this invention is the heat insulation box body which insulates the storage compartment and the outside of a storehouse, the 2nd condenser arrange | positioned at the front opening edge part of a compressor, a 1st condenser, and the said heat insulation box, and the front of the said heat insulation box body. And a refrigeration cycle having a flow path switching valve for switching a flow path to the second condenser and a flow path to the third condenser and a pressure reducing means and an evaporator installed at a place other than the opening edge, to circulate the refrigerant. A refrigerator, the blocking means provided between the flow path downstream of the second condenser and the flow path downstream of the third condenser and the evaporator, and a second control unit controlling to close the blocking means when the compressor stops operating. Equipped with.

The freezer which concerns on 4th this invention applies the refrigerator which concerns on 2nd this invention to a freezer.

According to the present invention, a refrigerator and a freezer having high energy saving performance can be provided by suppressing the inflow of a high temperature refrigerant that becomes a heat load from the condenser to the evaporator when the compressor is stopped.

BRIEF DESCRIPTION OF THE DRAWINGS The front view which shows the refrigerator of Embodiment 1 which concerns on this invention.
FIG. 2 is a sectional view taken along the line XX of FIG. 1 showing the configuration of the refrigerator of the first embodiment.
3 is a diagram illustrating a configuration of a refrigeration cycle of the refrigerator according to the first embodiment.
4 is a perspective view illustrating an arrangement position of a heat dissipation pipe in the refrigerator of the first embodiment;
5 is a control flowchart showing control during the cooling operation of the refrigerators of the first and second embodiments;
6 is a control flowchart showing control during the cooling operation of the refrigerator of the first embodiment;
7 is a control flowchart illustrating control during the cooling operation of the refrigerators of the first and second embodiments.
8A to 8E are control time charts of the refrigerator according to the first embodiment.
FIG. 9 is a diagram illustrating a configuration of a refrigeration cycle of the refrigerator according to the second embodiment. FIG.
10 is a flowchart showing control during the cooling operation of the refrigerator according to the second embodiment;
11A to 11E are control time charts of the refrigerator according to the second embodiment.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described with reference to an accompanying drawing.

<< Embodiment 1 >>

BRIEF DESCRIPTION OF THE DRAWINGS It is a front view which shows the refrigerator of Embodiment 1 which concerns on this invention, and FIG. 2 is X-X sectional drawing of FIG. 1 which shows the structure of the refrigerator.

In the refrigerator 1 of Embodiment 1, in the refrigerator main body 1H which comprises the main-body part, the refrigerating chamber 2, the ice-making chamber 3 and the upper freezer compartment 4, the lower freezer compartment 5, and the vegetable compartment (from the upper part) 6) is provided. In addition, the ice-making chamber 3 and the upper end freezing chamber 4 are arranged side by side between the refrigerating chamber 2 and the lower end freezing chamber 5.

The refrigerator compartment 2 and the vegetable compartment 6 are storage compartments of the refrigeration temperature range of about 3-5 degreeC. On the other hand, the ice making chamber 3, the upper freezer compartment 4, and the lower freezer compartment 5 are storage rooms of the freezing temperature range of about -18 degreeC.

The refrigerating chamber 2 is equipped with the door (a so-called French type) of refrigerating chamber doors 2a and 2b divided | segmented to the left and right on the front side.

The ice-making chamber 3, the upper freezer compartment 4, the lower freezer compartment 5, and the vegetable compartment 6 are each withdrawable-type ice-making door 3a, the upper freezer door 4a, the lower freezer door 5a, And a vegetable compartment door 6a.

Moreover, the sealing member (shown in the form along the outer edge of each door) is formed in the surface by the side of the storage chambers 2, 3, 4, 5, 6 in each door 2a, 2b, 3a, 4a, 5a, 6a. And the entry of warm outside air into the storage compartment and the leakage of cold air from the storage compartment at the time of closing of each door.

The refrigerator main body 1H is a door sensor (not shown) which detects the opening / closing state of the doors 2a, 2b, 3a, 4a, 5a, and 6a provided in each of the storage compartments 2, 3, 4, 5, and 6, respectively. And an alarm (not shown) for notifying a user (user) when the state judged that each door is open continues for a predetermined time, for example, 1 minute or more.

In addition, the refrigerator main body 1H is provided with the temperature setter etc. (not shown) for a user to set the temperature of the refrigerating chamber 2, the temperature setting of the upper freezer compartment 4, the lower freezer compartment 5, and the like. have.

As shown in FIG. 2, the inside and outside of the refrigerator main body 1H are disposed between the outer box 1a which forms the outline of the refrigerator 1 and the inner box 1b which forms the storage compartments 2 to 6. It is spaced apart by the heat insulation box 10 formed by filling a foam heat insulation material (foamed polyurethane). The heat insulation box 10 mounts the vacuum heat insulating material 25 with high heat insulation other than the foamed heat insulating material to be filled.

In the refrigerator main body 1H, the refrigerating chamber 2 of the refrigerating temperature zone, the upper end freezing chamber 4 of the refrigerating temperature zone, and the ice making chamber 3 (refer FIG. 1) are thermally partitioned by the upper insulation partition wall 51. It is installed.

Moreover, the lower freezing compartment 5 of the refrigeration temperature zone and the vegetable compartment 6 of the refrigeration temperature zone are partitioned insulated by the lower heat insulation partition wall 52.

As shown by the broken line of FIG. 1, the upper part of the lower freezer compartment 5 is the horizontal compartment 53 which divides the lower freezer compartment 5, the ice-making chamber 3, and the upper end freezer compartment 4 in the up-down direction (FIG. 2).

As shown in FIG. 1, the vertical section 54 is provided on the upper side of the horizontal section 53 to divide the ice making chamber 3 and the upper end freezing chamber 4 in the left-right direction. 2, the vertical section 54 is abbreviate | omitted and shown.

As shown in FIG. 2, the lateral compartment 53 includes the front surface (the left side in FIG. 2) of the lower insulation partition wall 52 and the left and right side walls 1H1 and 1H2 (FIG. 2) of the refrigerator main body 1H (FIG. 1) and a seal member (not shown) provided on the side of the lower freezer compartment 5 side of the lower freezer compartment 5a, and received between the lower freezer compartment 5 and the lower freezer compartment door 5a. Suppresses the movement of gas in and out of

In addition, the sealing member (not shown) provided in the storage chamber (ice-making chamber 3 and the upper-side freezer compartment 4) side of the ice-making chamber door 3a and the upper freezer compartment door 4a is the horizontal compartment 53 ), The vertical section 54, the upper insulation partition wall 51 and the front face of the left and right side walls 1H1 and 1H2 (see Fig. 1) of the refrigerator main body 1H, thereby making the ice making chamber 3 and The movement (entry / in) of the gas between the upper freezing chamber 4 and the ice making chamber door 3a and the upper freezing chamber door 4a is suppressed, respectively.

In addition, since the ice-making chamber 3, the upper freezer compartment 4, and the lower freezer compartment 5 are all freezing temperature zones, the horizontal division part 53 and the vertical division part 54 of FIG. In order to receive the sealing member of the door 3a and the upper freezer door 4a, it should just be at least in front of the refrigerator main body 1H (refer FIG. 2). That is, since the ice making chamber 3, the upper freezer compartment 4, and the lower freezer compartment 5 of the freezing temperature zone are the same freezing temperature zone, there may be a movement (entry in and out) of the gas between the storage compartments, and there is no need for adiabatic partitioning. .

On the other hand, in the case where the upper freezer compartment 4 is used as a temperature switching chamber, since the upper freezer compartment 4 is switched between the freezing temperature zone and the refrigerating temperature zone, it is necessary to insulate and partition the ice making chamber 3 and the lower freezer compartment 5 from each other. . In this case, the horizontal section 53 and the vertical section 54 extend from the front side of the refrigerator main body 1H to the rear wall 1H3 (see FIG. 2).

Inside the refrigerating chamber 2 of the refrigerating chamber doors 2a and 2b shown in FIG. 1, as shown in FIG. 2, the some door pocket 32 is provided. In the refrigerating chamber 2, a plurality of shelves 36 are provided, and the refrigerating chamber 2 is partitioned into a plurality of storage spaces in the longitudinal direction by the shelves 36.

In the ice making chamber 3, the upper freezer compartment 4, the lower freezer compartment 5, and the vegetable compartment 6, storage containers 3b, 4b, 5b, 6b are provided, respectively, and the door provided in front of each storage compartment. It moves (goes in and out) integrally with (3a, 4a, 5a, 6a) integrally.

That is, the ice cream door 3a, the upper freezing compartment door 4a, the lower freezing compartment door 5a, and the vegetable compartment door 6a are drawn out to the front side by the user's hand on a handle (not shown) provided on the front face, respectively. As a result, each of the storage containers 3b, 4b, 5b, and 6b of the ice making chamber 3, the upper freezing chamber 4, the lower freezing chamber 5, and the vegetable chamber 6 is located on the front side (left side of the paper in Fig. 2). ) Is the configuration withdrawn.

3 is a diagram illustrating a configuration of a refrigeration cycle of the refrigerator according to the first embodiment.

The refrigerator 1 is a cooling means for cooling the inside of the refrigerator, and the evaporator 7 is provided in the evaporator storage chamber 8 provided in the substantially rear portion (see FIG. 2) of the lower freezer compartment 5. As an example of the evaporator 7, there is a fin tube heat exchanger.

Blowing means which circulates the air cooled by the evaporator 7 (henceforth the low-temperature air heat-exchanged by the evaporator 7 is called "cold air") in the inside of the evaporator 7 in the evaporator accommodating chamber 8 inside. As an inside, a blower 9 is provided. As an example of the in-air blower 9, a propeller fan is mentioned.

As shown in FIG. 2, the cold air cooled by heat exchange with the refrigerant flowing through the evaporator 7 is arranged at the rear side of each storage chamber 2, 6, 3, 4, 5 by the internal blower 9. Through the refrigerator compartment ventilation duct 11, the vegetable compartment ventilation duct (not shown), and the freezer compartment ventilation duct 12, respectively, the refrigerator compartment 2, the vegetable compartment 6, the ice-making compartment 3, the upper freezer compartment 4, and the lower freezer compartment It is sent to each storage room of (5).

Blowing air into each of the storage compartments 2, 6, 3, 4, and 5 includes a refrigerator compartment damper 80 for controlling the blowing amount to the refrigerating chamber 2, and a vegetable chamber damper (not shown) for controlling the blowing amount to the vegetable compartment 6 ( The blower is opened and closed by the cold air adjusting means) and the freezer compartment damper 81 which controls the air blowing amount to the ice making chamber 3, the upper freezer compartment 4, and the lower freezer compartment 5 of the freezing temperature range.

When blowing to the refrigerating chamber 2 is performed when the refrigerating chamber damper 80 (refer FIG. 2) is open, the cold air is blown out 2c via the refrigerating chamber blowing duct 11 behind the refrigerating chamber 2 2) is sent to the refrigerating chamber 2 from the case where there are three jet ports 2c. The cold air which cooled the refrigerator compartment 2 passes through the refrigerator compartment return duct (not shown) arrange | positioned to the side of the evaporator storage chamber 8 from the refrigerator compartment return port (not shown) provided in the lower part of the refrigerator compartment 2, and the evaporator It returns to the lower part of the storage chamber 8 (back).

When blowing to the lowermost vegetable chamber 6 of the refrigerator 1 in the open state of the vegetable chamber damper which is not shown in figure, cold air passes through a vegetable chamber blowing duct to the vegetable chamber 6 (not shown). It is blown. The cold air which cooled the vegetable compartment 6 passes through the vegetable compartment return duct 18 from the vegetable compartment return duct inlet 18b provided in the lower front of the lower side insulation partition wall 52, and stores the evaporator from the vegetable compartment return duct outlet 18a. It returns to the lower part of the thread 8 (returns).

In front of the evaporator storage chamber 8, a partition member 13 for partitioning between the ice making chamber 3, the upper freezer chamber 4, the lower freezer chamber 5 and the evaporator storage chamber 8 of the refrigerating temperature chamber is provided. have. Blowing ports 3c, 4c, and 5c are formed in the partition member 13.

When the freezer compartment damper 81 is in an open state, the cold air is not shown in the ice making chamber blowing duct behind the ice making chamber 3, the upper freezing chamber blowing duct 16 behind the upper freezing chamber 4, and the lower freezing chamber 5. It flows through the lower lower end freezer compartment ventilation duct 12, and is blown from the blower opening 3c, 4c, 5c to the ice-making chamber 3, the upper end freezer compartment 4, and the lower end freezer compartment 5, respectively.

The partition member 13 is provided with a freezer compartment return port 17 at a position in the lower inner side of the lower freezer compartment 5, and the ice making chamber 3, the top freezer compartment 4, and the bottom freezer compartment 5 of the freezing temperature chamber. The cold air which has cooled down is introduced into the evaporator accommodating chamber 8 through the freezer compartment return port 17. In addition, the freezer compartment return port 17 has a width dimension substantially the same as the width of the evaporator 7 (up and down direction of the paper surface in FIG. 2).

Generally, cold air having a low temperature with respect to ambient temperature has a high density because of low kinetic energy of air molecules, and high temperature air has a low density because of high kinetic energy. Forms a stream. Accordingly, by supplying more cold air above the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5 of the storage chamber, the inside of the storage chamber can be efficiently and satisfactorily cooled by the action of the downward flow.

In the present refrigerator 1, the freezing chamber damper 81 is disposed above the in-vehicle blower 9 behind the upper freezer compartment 4 to smoothly blow the air from the in-vehicle blower 9. The upper freezer compartment 4 is configured to blow air from the upper portion thereof. And the downward flow of cold air from the upper part of the ice-making chamber 3 or the upper freezer compartment 4 to the lower freezer compartment 5 by making the structure which the ice-making chamber 3, the upper freezer compartment 4, and the lower freezer compartment 5 communicate. Can increase the cooling effect.

<Freezing cycle (1S)>

Next, the refrigerating cycle 1S according to the first embodiment will be described with reference to FIGS. 3 and 4 and appropriately with reference to FIG. 2.

4 is a perspective view illustrating an arrangement position of a heat dissipation pipe in the refrigerator of the first embodiment.

The refrigerator 1 is equipped with the refrigeration cycle 1S shown in FIG. 3 through which a refrigerant | coolant flows in order to cool the storage chambers 2, 3, 4, 5, 6 (refer FIG. 1).

The refrigeration cycle 1S includes a compressor 24 for compressing the refrigerant, heat dissipation means 60 (61, 62, 63, 64) for dissipating heat of the refrigerant sent from the compressor 24, and heat dissipation means 60 The capillary tube 43 of the decompression means for decompressing the refrigerant sent from the e) and the evaporator 7 of the cooling means for cooling the air with the refrigerant sent from the capillary tube 43 are sequentially connected by the pipe 68. have. The refrigerant of the heat medium flows (circulates) through the pipe 68 to which the compressor 24, the heat dissipation means 60, the capillary tube 43, and the evaporator 7 are connected.

The compressor 24 compresses the low temperature and low pressure refrigerant to high temperature and high pressure. As shown in FIG. 2, the compressor 24 is provided in the machine room 19 provided in the lower back of the refrigerator main body 1H.

The evaporator 7 cools the air flowing in the evaporator accommodating chamber 8 (takes heat of vaporization from the air) by the latent heat of the refrigerant evaporated from the capillary tube 43 and evaporates. 3, 4, 5, 6) to supply the cold air.

The heat dissipation means 60 shown in FIG. 3 is the condenser 61 (refer FIG. 3, not shown in FIG. 2) arrange | positioned in the machine room 19 (refer FIG. 2) arrange | positioned at the rear lower part of the refrigerator 1. And heat dissipation pipes 62, 63, and 64.

An example of the condenser 61 is a fin tube heat exchanger. In the machine room 19, the ultra-high blower 26 (refer FIG. 3, not shown in FIG. 2) is arrange | positioned, and the heat dissipation of the condenser 61 is promoted by operating the ultra-high blower 26. FIG.

The heat dissipation pipe 62 shown in FIG. 3 is formed on the surface of the outer box 1a of the heat insulating box 10 (see FIG. 4) between the outer box 1a and the inner box 1b shown in FIG. 2. It is arranged to be in contact. That is, the heat dissipation pipe 62 (indicated by the thick broken line in FIG. 4) connected to the condenser 61 (see FIG. 3) in the machine room 19 emerges from the inside of the machine room 19 and is attached to the outer box 1a surface. In contact with each other, the left side surface 10h of the thermal insulation box 10 is disposed up and down, and the right side surface 10m is disposed up and down over the front portion of the ceiling surface 10t, and the rear surface 10s thereof (in FIG. 4). It is arranged in a thin broken line) and enters the machine room 19 again and is connected to the three-way valve 65 in the machine room 19.

In addition, in FIG. 3, although the heat radiation pipe 62 arrange | positioned at the left side surface 10h and the right side surface 10m of the heat insulation box 10 and the back surface 10s is the same thing, it is thick By using a dashed line and a thin dashed line, it is easy to see a drawing. Therefore, it is originally the heat radiation pipe 62 of the same pipe of the same diameter.

The outer box 1a is made of steel sheet, and the heat dissipation pipe 62 is disposed in contact with the inner surface of the outer box 1a, so that the heat of the heat dissipation pipe 62 conducts the outer box 1a, and thus the outer box 1a. ) It radiates well to the outside air from the outer surface.

The heat insulation pipe 64 (indicated with a bold line in FIG. 4) connected to the heat radiation pipe 62 via the three-way valve 65 is the upper side heat insulation section shown by the dashed-dotted line in FIG. 4 of the heat insulation box 10. As shown in FIG. It is arrange | positioned at each inner front edge part (front opening edge part) of the wall 51, the lower heat insulation partition wall 52, the horizontal division part 53, and the longitudinal division part 54. As shown in FIG.

These partition walls (compartments) 51, 52, 53, 54 are low temperature because they are in contact with the storage compartments 2, 3, 4, 5, 6, but in front of the partition walls 51, 52, 53, 54. The part is disposed in the opening edge portion of each of the storage chambers 2, 3, 4, 5, 6, and is easily contacted with the outside air by opening and closing the doors 2a, 2b, 3a, 4a, 5a, 6a by the user. Therefore, when the front opening edge surface temperature of the partition walls 51, 52, 53, 54 becomes below the dew point temperature of external air, there exists a possibility that dew condensation may arise.

Therefore, condensation prevention to the front opening edge of the refrigerator main body 1H (in particular, the front part of the upper heat insulation partition wall 51, the lower heat insulation partition wall 52, the horizontal compartment part 53, and the vertical compartment part 54) is prevented. For this purpose, the heat dissipation pipe 64 is disposed to dissipate heat of the high-temperature refrigerant, thereby preventing the front opening edge of the refrigerator main body 1H from being below the dew point temperature.

Inside the machine room 19, the 3-way valve 65 (refer FIG. 3) is arrange | positioned as a heat radiation performance control means. The outlet portion 62o of the heat dissipation pipe 62 enters the machine room 19 and is connected to the inlet 65a of the three-way valve 65.

The three-way valve 65 is comprised from one inlet 65a and two outlets 65b and 65c.

The three-way valve 65 flows the refrigerant flowing from the inlet 65a into the (1) outlet 65b (inlet 65a open state, outlet 65b open state, outlet 65c closed state). (2) The state which flows into the exit 65c (the inlet 65a open state, the outlet 65b closed state, the outlet 65c open state), (3) The state which does not flow in both the outlet 65b, 65c [ Inlet 65a open state, outlet 65b closed state, outlet 65c closed state], (4) states flowing through both of the outlets 65b, 65c (inlet 65a open state, outlet 65b open state) And an outlet 65c in an open state].

The outlet 65b of the three-way valve 65 is an inlet 64i of the heat dissipation pipe 64, and the outlet 65c of the three-way valve 65 is an inlet 63i of the heat dissipation pipe 63, respectively. Connected.

The check valve 67 is arrange | positioned in the piping 68 of the outlet part 64o of the heat dissipation pipe 64, and the heat dissipation pipe (from the outlet part 63o of the late dryer 41 and the heat dissipation pipe 63) Backflow to 64 is prevented.

In the machine room 19, downstream of the check valve 67, the pipe 68 joins the outlet portion 63o of the heat dissipation pipe 63 and is connected to the dryer 41. The dryer 41 is for drying and absorbing moisture in the coolant, and the inside of the pipe 68 is frozen and blocked to prevent the coolant from circulating.

In addition, the portion of the pipe 68a, which is a part of the pipe 68 from the evaporator 7 toward the compressor 24, is brought into proximity or contact with the capillary tube 43, and the refrigerant in the capillary tube 43 facing the evaporator 7 is provided. The heat is transferred to the refrigerant in the pipe 68a.

The defrost heater 22 is provided below the evaporator storage chamber 8 shown in FIG. By energizing and heating the defrost heater 22, frost grown on the wall of the evaporator 7 and the evaporator storage chamber 8 in the vicinity thereof is dissolved (fused).

The defrost water generated by melting the frost flows into the groove portion 23 provided in the lower portion of the evaporator storage chamber 8 shown in FIG. 2, and then flows down the drain pipe 27 and is provided in the machine chamber 19. ) Is stored. The defrost water stored in the evaporating dish 21 is evaporated by the heat generation of the compressor 24 and the condenser 61 (refer FIG. 3) arranged inside the machine room 19.

As shown in FIG. 2, the upper part of the evaporator 7 includes an evaporator temperature sensor 35 attached to the evaporator 7, a refrigerating chamber temperature sensor 33 in the refrigerating chamber 2, and a freezing chamber in the lower freezing chamber 5. The temperature sensor 34 is provided, respectively, and detects the temperature of the evaporator 7, the temperature of the refrigerating chamber 2, and the temperature of the lower freezing chamber 5, respectively. The vegetable chamber temperature sensor 33a is also arranged in the vegetable chamber 6.

The refrigerating compartment temperature sensor 33, the vegetable compartment temperature sensor 33a, and the freezer compartment temperature sensor 34 are installed in a place where the ejection cold air to each of the storage compartments 2, 6, 3, and 4 is not directly closed, thereby improving detection accuracy. have.

Moreover, the refrigerator main body 1H is equipped with the outside air temperature sensor and outside air humidity sensor which are not shown which detect the ambient temperature and humidity environment (outdoor temperature, outside air humidity) in which the refrigerator 1 was installed.

<Control section>

On the upper surface side of the ceiling wall 1H0 of the refrigerator main body 1H shown in FIG. 2, a control including a CPU (Central Processing Unit), a ROM (Read Only Memory) or a RAM (Random Access Memory), an interface circuit, or the like is mounted. The board | substrate 31 is arrange | positioned. The interface circuit of the control board 31 includes the above-mentioned outside air temperature sensor, outside air humidity sensor, evaporator temperature sensor 35, freezer compartment temperature sensor 34, refrigerator compartment temperature sensor 33, vegetable compartment temperature sensor 33a, and each storage compartment. It is connected to the door sensor which detects the opening / closing state of the door 3a, 4a, 5a, 6a (refer FIG. 1), the temperature setter of each storage chamber 2, 4, 5 provided in the refrigerating chamber door 2a, etc., respectively.

By executing the control program stored in the ROM in advance, ON / OFF of the compressor 24, the three-way valve 65, the two-way valve 66 (refer to FIG. 9 of later embodiment 2), and the refrigerator compartment damper 80 ), Control of each actuator (not shown) for separately operating the vegetable compartment damper and the freezer compartment damper 81, the in-flight blower 9 (see FIG. 2) in the evaporator storage chamber 8 and the out-of-air blower 26 in the machine compartment 19. (ON / OFF control) and rotational speed control (see FIG. 3), alarm ON / OFF, etc. for notifying the open state of the doors 2a, 2b, 3a, 4a, 5a, 6 (see FIG. 1). Control is performed.

<Control during refrigeration operation of the refrigerator 1>

Next, control during the cooling operation in the refrigerator 1 of the first embodiment will be described with reference to FIGS. 5 to 7.

5-7 is a control flowchart which shows the control during the cooling operation of the refrigerator of Embodiment 1. FIG. 8A to 8E are control time charts of the refrigerator according to the first embodiment.

As described above, the control of the refrigerator 1 is performed by the CPU mounted on the control board 31 (see FIG. 2) executing a control program stored in the ROM.

As shown in FIG. 5, the refrigerator 1 starts operation by turning on the power (start), an outside air temperature sensor, an outside air humidity sensor, and temperature sensors 33, 34, 33a of respective storage compartments in the refrigerator (FIG. Based on the measured value of 2), the basic switching time tb, tc (time width) which flows refrigerant into the outlet 65b and the outlet 65c of the 3-way valve 65, respectively (step S101 of FIG. 5) is computed. ).

Next, it is determined whether or not the compressor 24 stop condition is satisfied (step S102). The compressor stop condition is satisfied when the temperature detected by the freezer compartment temperature sensor 34 is equal to or lower than Toff ° C (see FIG. 8A). Therefore, the compressor stop condition is incomplete when the temperature detected by the freezer compartment temperature sensor 34 is higher than Toff ° C.

When the compressor stop condition does not hold (NO in step S102), that is, when the temperature detected by the freezer compartment temperature sensor 34 is higher than Toff ° C, it is determined whether the three-way valve 65 switching condition is satisfied (step S102). S103). The conditions in which the three-way valve 65 cannot be switched include a plurality of three-way valves having a high outside air humidity, a plurality of rotational speeds (rotational speeds) of the compressor 24, a predetermined value or the like, and satisfying any one condition. It is determined that the switching condition is not satisfied. On the contrary, when the external air humidity satisfies all of a plurality of conditions such as less than the predetermined value and the rotational speed (rotation speed) of the compressor 24 is less than the predetermined value, it is determined that the three-way valve switching conditions are satisfied.

When the three-way valve switching condition is satisfied (YES in step S103), first, the three-way valve 65 in Fig. 3 is opened in the inlet 65a, the outlet 65b in the open state, and the outlet 65c in the closed state. (A → b), in order to warm the vicinity of the door and prevent condensation, the refrigerant is flowed into the heat radiation pipe 64 (times t0 to t11 in FIG. 8C) (step S104).

In the state where the compressor 24 is ON, it is determined whether the compressor stop condition is satisfied (step S105).

When the compressor stop condition is not satisfied (NO in step S105), that is, when the temperature detected by the freezer compartment temperature sensor 34 is equal to or lower than Toff ° C, after the step S104 is executed, the time tb (heat radiating pipe 64) It is determined whether or not the time for the coolant to flow through has passed] (step S106).

If the time tb has not passed (NO in step S106), it is determined whether or not the three-way valve switching condition is satisfied (step S107). As described above, there are a plurality of conditions such as a condition in which the three-way valve 65 cannot be switched, such as a high outside air humidity and a rotational speed (number) of the compressor 24 being a predetermined value or more. It is determined that the three-way valve switching conditions are not satisfied at the time point at which it is satisfied. On the contrary, when the external air humidity satisfies all of a plurality of conditions such as less than the predetermined value and the rotational speed (rotation speed) of the compressor 24 is less than the predetermined value, it is determined that the three-way valve switching conditions are satisfied.

If the three-way valve switching condition is satisfied (YES in step S107), the flow proceeds to step S105.

In step S106, when time tb (time to flow refrigerant into the heat dissipation pipe 64) elapses (YES in step S106), the three-way valve 65 is opened at the inlet 65a and the outlet 65b. A coolant flows into the heat dissipation pipe 63 in the closed state and the outlet 65c (opened state 65c) (time t14 in FIG. 8C) (step S108).

Next, it is determined whether or not the compressor stop condition is satisfied (step S109 in FIG. 5).

If the compressor stop condition does not hold (NO in step S109), it is determined whether time tc (time for flowing coolant into the heat radiating pipe 63) has elapsed after executing step S108 (step S110).

If the time tc (time for flowing coolant into the heat radiating pipe 63) has not elapsed (NO in step S110), it is determined whether or not the three-way valve switching condition is satisfied (step S111).

If the three-way valve switching condition is satisfied (YES in step S111), the flow proceeds to step S109.

In step S110, when time tc (time to flow refrigerant into the heat radiating pipe 63) has elapsed, the process proceeds to step S104 again, and the three-way valve 65 shown in FIG. 3 is opened in the inlet 65a and the outlet 65b. ) In the open state, the outlet 65c is closed, and the coolant flows through the heat dissipation pipe 64 (time t15 in FIG. 8C).

When the compressor stop condition is satisfied in steps S102, S105, and S109 of FIG. 5 (YES in steps S102, S105, and S109), the basic flows to the outlet 65b and the outlet 65c of the three-way valve 65, respectively. The switching time tb, tc is calculated again (step S112 of FIG. 6).

After the step S112, the three-way valve 65 is set to the inlet 65a open state, the outlet 65b closed state, and the outlet 65c closed state with the compressor 24 ON (Fig. 8 (c)). Time t11) (step S113 in FIG. 6).

Then, with reference to the values of the temperature sensors 33, 34, 33a of the respective storage chambers 2, 3, 4, 5, 6, before the compressor 24 stops, for every storage chamber 2, 4, 5, 6 It determines whether it is below the set threshold value (step S114 of FIG. 6), and checks whether the storage chambers 2, 3, 4, 5, 6 which are not cold enough exist.

If all the storage chambers are cooled below the threshold (YES in step S114), all dampers 80, 81 and other vegetable chamber dampers are closed (time t12 in Fig. 8E) (step S115a). .

In the case where the storage chamber having a temperature higher than or equal to the threshold exists among all the storage chambers 2, 3, 4, 5, and 6 (NO in step S114 of FIG. 6), the temperature blower 9 is turned ON and the temperature higher than the threshold. The damper corresponding to the storage compartment is opened (step S115b).

Thereafter, after the time ts has passed (YES in step S116), the compressor 24 is turned OFF (time t12 in FIG. 8B) (step S117). The technical meaning of time ts is later.

The process from step S113 to step S117 is performed to reduce the amount of refrigerant in the heat dissipation pipe 63, the heat dissipation pipe 64, and the capillary tube 43 shown in FIG. 3, and to flow downstream from the evaporator 7. By performing this control, even if the compressor 24 is stopped in step S117, since the amount of refrigerant remaining in the heat dissipation pipes 63 and 64 and the capillary tube 43 is small, the heat dissipation pipes 63 and 64 and the capillary tube Since the amount of the warm refrigerant entering the inside of the 43 into the evaporator 7 decreases, the heat load of the evaporator 7 also decreases, making it possible to improve the energy saving performance.

Since the refrigerant is discharged from the heat dissipation pipes 63 and 64 and the capillary tube 43 by the operation from the start of step S113 to the end of the process of step S117, it is defined as the refrigerant recovery.

Here, when the control of step S115a in FIG. 6 is performed during the refrigerant recovery, only the evaporator 7 is cooled without cooling all the storage chambers 2, 3, 4, 5, 6 with all dampers closed (claim 3). When the compressor 24 is turned ON next time, the temperature of the evaporator 7 is low, which makes it possible to quickly send cold air into the refrigerator, thereby enabling efficient operation.

In addition, in step S115a, you may comprise so that the air blower 9 may be turned OFF instead of closing all dampers (claim 3). Also in this case, since the cold air around the evaporator 7 is maintained, the temperature of the evaporator 7 when the compressor 24 is turned on next is low, which makes it possible to quickly send cold air to the inside of the refrigerator and improve efficiency. It has the effect of being able to drive.

On the other hand, when the control of step S115b of FIG. 6 is performed during the refrigerant recovery (claim 2), while the refrigerant remaining in the heat dissipation pipe 63 and the heat dissipation pipe 64 is depressurized and introduced into the evaporator 7, the cooling capacity is reduced. In addition, since the cooling in the refrigerator can be performed, the temperature rise in the refrigerator during the refrigerant recovery can be suppressed.

The time ts (the time t11-t12 of FIG.8 (c)) in step S116 shows the time to collect | recover refrigerant. Specifically, in the refrigerator 1, the refrigerant recovery time ts is 4 minutes.

If the refrigerant recovery time ts is too short, the compressor 24 is turned off without recovering the refrigerant remaining in the heat radiation pipe 63, the heat radiation pipe 64, and the capillary tube 43, so that the remaining refrigerant evaporates the evaporator 7. To deteriorate energy-saving performance.

On the contrary, when the refrigerant recovery time ts is too long, not only the power consumption is consumed for the idle operation of the compressor 24, but also the energy saving performance is deteriorated, and the temperature in the refrigerator rises. For this reason, since an appropriate refrigerant recovery time ts changes according to the volume in the pipes, such as the heat radiation pipes 63 and 64, the rotational speed (rotation speed) of the compressor 24, etc., the refrigerant recovery time ts is an appropriate value in accordance with individual conditions. You need to.

After the compressor 24 is stopped (step S117), the compressor 24 remains stopped until the compressor starting condition is satisfied (YES in step S118) (time t12 in Fig. 8B). T13) (step Sl17 of FIG. 6). That is, the compressor 24 is stopped until the temperature detected by the freezer compartment temperature sensor 34 becomes higher than Toff ° C. (compressor starting condition is established).

When the compressor starting condition is satisfied (YES in step S118), the three-way valve 65 is placed in the inlet 65a open state, the outlet 65b open state, and the outlet 65c closed state (a → b). The refrigerant 24 flows into the heat dissipation pipe 64 (see FIG. 3) and simultaneously starts the compressor 24 (times t13 in FIGS. 8B and 8C (step S119), and the process proceeds to step S105 in FIG. 5. do.

On the other hand, if the compressor starting condition does not hold (NO in step S118), the determination as to whether or not the compressor starting condition of step S118 is satisfied is continued.

If the three-way valve switching conditions do not hold in Steps S103, S107, S111, etc. of FIG. 5, the flow advances to Step S120 of FIG. 7, and the three-way valve 65 is opened in the inlet 65a and the outlet 65b in the open state. The coolant is flowed into the heat radiating pipe 64 in a state where the outlet 65c is closed.

Thereafter, it is determined whether or not the compressor stop condition is satisfied (step S121 in FIG. 7).

If the compressor stop condition does not hold (NO in step S121), it is determined whether or not the three-way valve switching condition holds (step S122 in Fig. 7).

If the three-way valve switching condition does not hold (NO in step S122), the flow proceeds to step S121 (return).

On the other hand, when the three-way valve switching condition is satisfied (YES in step S122), step S104 in Fig. 5 is executed.

In step S121, when the compressor stop condition is satisfied, the process proceeds to step S112 in FIG.

<Basic switching time tb, tc of the three-way valve 65>

Next, the basic switching time tb of the three-way valve 65 shown in FIG. 8C (the three-way valve 65 is opened in the inlet 65a, the outlet 65b is opened, and the outlet 65c is closed). Time to state] and basic switching time tc (time to set the three-way valve 65 to the inlet 65a open state, the outlet 65b closed state, and the outlet 65c open state) will be described.

In the first embodiment, the timing for switching the three-way valve 65 is basically controlled by time.

The basic switching time tb of FIG. 8C is the time (time width) which flows refrigerant into the heat radiation pipe 64 of FIG. 3, and passes the condenser 61 and the heat radiation pipe 62 downstream of the compressor 24. FIG. The high temperature refrigerant flows through the heat dissipation pipe 64 disposed in the front opening edge portion of the refrigerator main body 1H (insulation box body 10) to raise the temperature of the front opening edge by heat transfer of the high temperature refrigerant.

The basic switching time tc in FIG. 8C is the time (time width) of flowing the refrigerant through the heat dissipation pipe 63 (see FIG. 3), during which the front opening edge (part) of the refrigerator main body 1H is inside the refrigerator. Since it cools by cold air from, there exists a possibility that dew may generate | occur | produce below the dew point temperature depending on an outdoor air temperature and outdoor air humidity.

Therefore, it is necessary to raise the temperature of the front opening edge (part) in accordance with the outside air temperature and the outside air humidity in order to prevent dew attachment.

By the way, since heat invasion from the heat dissipation pipe 64 into the interior (storage chambers 2, 3, 4, 5, 6), there is also a problem such that the temperature in the interior becomes difficult to cool. Therefore, flowing high temperature refrigerant for a long time in the heat radiation pipe 64 deteriorates energy saving performance, and therefore is not preferable. Therefore, the basic switching time tb which flows a high temperature refrigerant | coolant into the heat radiation pipe 64 (refer FIG. 3, FIG. 4) aims at the time from the beginning of flowing a refrigerant | coolant until the temperature of a front opening edge fully rises. It is desirable to.

On the other hand, the basic switching time tc which flows a high temperature refrigerant | coolant into the heat radiating pipe 63 (refer FIG. 3), dew | dew on the front opening edge of the refrigerator main body 1H based on the dew point temperature which can be computed from outside temperature and outside air humidity. It is desirable to check and determine the time it is not attached. In this refrigerator 1, the basic switching time tb and tc are specifically made into tb = 15 minutes and tc = 20 minutes, when the outdoor temperature is 30 degreeC and the outdoor humidity is 70%. In addition, these numerical values are an example and can be arbitrarily set.

Here, while the compressor 24 is OFF, since the compressor 24 does not make a high temperature and high pressure refrigerant | coolant, the front of the refrigerator main body 1H (insulation box body 10) by the refrigerant which flows through the heat radiation pipe 64 is carried out. The temperature rise of the opening edge is also eliminated. Therefore, during the OFF time tcoff (refer to FIG. 8 (b)) of the compressor 24, the temperature of the front opening edge continues to fall by the cold temperature in a refrigerator.

After step S108 in FIG. 5, if step S109 is established just before time tc has elapsed, the time for not heating the front opening edge is about tc + tcoff (see FIGS. 8B and 8C). There is a possibility that the temperature of the front opening edge drops too much and condensation occurs.

Therefore, in the refrigerator 1, when the detection temperature of the freezer compartment temperature sensor 34 becomes Toff ° C or lower, the compressor stop condition is satisfied. Therefore, when the freezer compartment temperature sensor is a temperature of Tfix (≥Toff) ° C or lower, The three-way valve switchable condition is made incomplete (step S107 in FIG. 5) (claim 6).

Thereby, since the temperature of the front opening edge of refrigerator main body 1H (insulation box body 10) rises immediately before a compressor stop condition is established, the possibility of dew condensation will reduce.

After that, when the compressor 24 is turned off or when the freezer compartment temperature sensor becomes higher than Tfixt, the three-way valve switchable condition is released again (see S107 in FIG. 5, S122 in FIG. 7, etc.) (claim 7) . Thereby, it can return to the structure of the dew attachment prevention of the front opening edge of the heat insulation box 10 (refrigerator main body 1H).

Here, although the basic switching time tb, tc becomes short, it becomes easy to adjust the temperature of the front opening edge of the refrigerator main body 1H (insulation box body 10), but the operation frequency of the three-way valve 65 increases, This causes the life of the three-way valve 65 to be shortened.

Therefore, taking into account that the life of the three-way valve 65 cannot be ignored, the number of times the three-way valve 65 has been operated is recorded in the ROM (e.g., the total number of euro switching count storage means), and the number of times exceeds a certain value. In this case, the lifespan of the three-way valve 65 is extended by lengthening the basic switching times tb and tc so as not to impair energy saving performance.

In addition, the basic switching time tb, tc is according to the temperature which the internal temperature detection means (freezer compartment temperature sensor 34, refrigerator compartment temperature sensor 33, vegetable compartment temperature sensor 33a) which detects the temperature of a storage compartment detects, Or it lengthens according to the average temperature set value of the storage chambers 2, 4, 5 which the user adjusted with the temperature setter (reservoir temperature control means) (claim 9). Thereby, the life of the three-way valve 65 can be extended.

Alternatively, by combining these conditions, it is also possible to lengthen the basic switching times tb and tc to extend the life of the three-way valve 65.

In addition, as shown in FIG. 8D, the refrigerator 1 has a heat dissipation pipe (a second c) as compared with when a coolant is flowing to the heat dissipation pipe (third condenser) 63 side (a → c). When the coolant is flowing to the side of the condenser 64, the rotation speed (number) of the blower 26 for the machine room at (a → b) is controlled to be lowered (claim 8). As a result, when the coolant is flowing to the heat dissipation pipe (third condenser) 63 side (a → c), the rotational speed (number) of the machine room blower 26 is increased to dissipate heat from the heat dissipation pipe 63. You can supplement.

According to the refrigerator 1 of Embodiment 1, before stopping the operation of the compressor 24, in the flow path switching valve 65, the heat radiation pipe (second condenser) 64 side and the heat radiation pipe (third condenser) ( After closing the flow path to the 63 side for a predetermined time, the operation of the compressor 24 is stopped to control the refrigerant recovery to reduce the amount of refrigerant in the heat radiation pipe 64 and the heat radiation pipe (third condenser) 63 ( Claim 1). As a result, it is possible to prevent the high temperature refrigerant from flowing into the cooler 7 and to conserve energy of the refrigerator 1.

In addition, the refrigerator 1 includes an internal blower 9 for blowing cold air of the evaporator 7 into the inside of the refrigerator, and a damper for adjusting the amount of cold air supplied to the storage chambers 2, 3, 4, 5, 6. Adjustment means) 80, 81, and closes the flow path to the heat dissipation pipe 64 side and the heat dissipation pipe 63 side for a predetermined time in the flow path switching valve 65 before the operation of the compressor 24 is stopped. During the refrigerant recovery, the dampers (cold air adjusting means) 80, 81 are controlled in a state of supplying cold air to the storage chambers 2, 3, 4, 5, 6, and the cold air is blown by the air blower 9. Control (claim 2). Therefore, the storage chambers 2, 3, 4, 5, 6 can be cooled by the cold inside the evaporator storage chamber 8, and it can maintain a low temperature state.

In addition, the refrigerator 1 during the refrigerant | coolant recovery which closes the flow path to the heat dissipation pipe 64 side and the heat dissipation pipe 63 side in a flow path switching valve 65 at a certain time, before stopping the operation of the compressor 24, The dampers (cold air adjusting means) 80, 81 for adjusting the amount of cold air supplied to the storage chambers 2, 3, 4, 5, 6 are closed, or the air blower 9 is turned off. It is controlled so as not to blow cold air into the storage compartments 2, 3, 4, 5, and 6 (claim 3). Therefore, it is possible to maintain the cold air in the evaporator storage chamber 8, to maintain the low temperature state of the cooler 7, and to smoothly transition to the cooling operation at the start of cooling of the next cooler 7. .

<< Embodiment 2 >>

The refrigerator 1 of the second embodiment replaces the control for closing the outlets 65b and 65c of the three-way valve 65 of the first embodiment before the compressor 24 is stopped, and thus the heat dissipation pipes 63 and 64. The two-way valve 6 of the shutoff means is provided on the evaporator side of the flow path downstream of the), and the two-way valve 6 is closed before the compressor 24 is stopped.

In addition, below, only the part from which the structure or control differs from the refrigerator 1 of Embodiment 1 is demonstrated, and the same component as that of Embodiment 1 or the same control step is given the same number, and the detailed description is Omit.

It is a figure which shows the structure of the refrigerating cycle of the refrigerator of Embodiment 2. FIG.

In the refrigerating cycle 2S of the second embodiment, a two-way valve 66 is provided on the downstream side of the dryer 41 downstream of the coupling portion of the flow path downstream of the heat dissipation pipes 63 and 64 as a refrigerant flow rate adjusting means. have.

Next, the difference part in a control method is demonstrated.

The control flowchart of Embodiment 2 is shown in FIG. 5, FIG. 7, and FIG. 5 and 7 are the same control as those in the first embodiment, and the control in FIG. 10 is specific to the second embodiment. 6 is specific to the first embodiment.

11A to 11E are control time charts of the refrigerator according to the second embodiment.

The difference from the first embodiment is the control after the compressor stop condition is established.

The control of the refrigerator 1 of Embodiment 2 is demonstrated with reference to FIG. 5, FIG. 7, and FIG.

When the compressor stop condition is satisfied in step S102 of FIG. 5 or the like (YES in step S102), the flow advances to step S123 of FIG. 10 to calculate the basic switching times tb and tc of the three-way valve 65. The two-way valve 66 is closed (time t21 in FIG. 11E), and the compressor 24 is turned OFF (time t21 in FIG. 11B) (step S124).

Thereby, the high temperature refrigerant | coolant in the heat dissipation pipe 63 and heat dissipation pipe 64 of FIG. 9 does not flow into the evaporator 7 because the 2-way valve 66 is closed.

In the second embodiment, the three-way valve 65 is switched to the inlet 65a open state, the outlet 65b open state, and the outlet 65c closed state in step S124, and the high temperature refrigerant in the heat dissipation pipe 62 is closed. Flows into the heat dissipation pipe 64 (claim 5). As a result, the high temperature refrigerant in the condenser 61 and the heat dissipation pipe 62 flows into the heat dissipation pipe 64, so that even if the temperature of the front opening edge of the refrigerator main body 1H (heat insulation box 10) is at the compressor stop. It becomes hard to go down, and it can make it hard to generate condensation of a front opening edge.

Next, while the compressor 24 is OFF (times t21 to t22 in FIG. 11B), the three-way valve 65 is not switched but the compressor starting condition is determined (continued). (Step S125).

On the other hand, when the compressor start condition is satisfied (YES in step S125), the two-way valve 66 is opened (time t22 in Fig. 11E), and the compressor 24 is started ON (Fig. Time t22) (step S126) of 11 (b).

According to the refrigerator 1 of Embodiment 2, 2 provided between the flow path downstream of the heat dissipation pipe (2nd condenser) 64, and the flow path downstream of the heat dissipation pipe (third condenser) 63, and the evaporator 7. Since the directional valve is controlled to close the two-way valve 66 when the compressor 24 stops operating, it is possible to suppress the high temperature refrigerant from flowing into the cooler 7 (claim 4). Therefore, cooling in the inside of the refrigerator by the cooler 7 can be performed smoothly, and energy saving of the refrigerator 1 can be aimed at.

In addition, the refrigerator 1 switches the flow path switching valve 65 to the heat radiation pipe (second condenser) 64 side when the compressor 24 stops (claim 5). Therefore, the remaining high temperature refrigerant flows through the heat dissipation pipe 64, so that the temperature of the front opening edge of the heat insulation box 10 (refrigerator main body 1H) rises, and dew adhesion can be suppressed.

According to the refrigerator 1 of Embodiment 1, 2, since the high temperature refrigerant | coolant which becomes a heat load from a condenser to a evaporator at the time of a compressor stop is suppressed, the increase of the heat load by the inflow of a high temperature refrigerant | coolant is suppressed, and energy saving performance is high. A refrigerator can be provided.

<< other embodiment >>

In the first and second embodiments, a two-way valve 66 is provided as a blocking means between the heat dissipation pipe (second condenser) 64 and the heat dissipation pipe (third condenser) 63 and the evaporator 7. Although the case where it installed was illustrated, you may use arbitrary things, such as three-way valves other than the two-way valve 66, as a blocking means, as long as the function of the interruption | blocking of a shutoff means can be achieved.

In addition, in the said Embodiment 1, 2, although the refrigerator provided with the freezer compartment and the refrigerator compartment was demonstrated and demonstrated, this invention is applicable also to the refrigerator provided only with a refrigerator compartment. In addition, the present invention can also be effectively applied to a freezer having only a freezer compartment.

1: refrigerator
2: cold storage room
3: ice making room (storage room)
4: upper freezer (storage room)
5: lower freezer (storage room)
6: vegetable room (storage room)
7: evaporator
9: blower in the air (interior blower)
10: insulation box
19: machine room
24: compressor
26: extra blower (machine room blower)
31: control board (1st control part, 2nd control part, 3rd control part, 4th control part, 5th control part, 6th control part)
33: refrigerator compartment temperature sensor (high temperature detection means)
33a: vegetable chamber temperature sensor (high temperature detection means)
34: freezer temperature sensor (high temperature detection means)
43 capillary tube (decompression means)
51: upper insulation partition wall (front opening edge)
52: lower insulation partition wall (front opening edge)
53: horizontal compartment (front opening edge)
54: vertical section (front opening edge)
61: condenser (first condenser)
62: heat dissipation pipe (first condenser)
63: heat dissipation pipe (third condenser)
64: heat dissipation pipe (second condenser)
65: 3-way valve (euro switching valve)
66: 2-way valve (blocking means)
68: piping (euro)
80: refrigerator compartment damper (cold air adjusting means)
81: freezer damper (cold air adjusting means)
1S, 2S: Refrigeration Cycle

Claims (6)

The heat insulation box which insulates the storage room and the outside in the storehouse,
A second condenser disposed at the front opening edge of the heat insulating box, and a third condenser provided at a place other than the front opening edge of the heat insulating box, and the flow path to the second condenser and the first condenser. 3 is a refrigerator having a flow path switching valve for switching the flow path to the condenser, a refrigeration cycle having a decompression means and an evaporator and circulating the refrigerant,
Blocking means provided between the flow path downstream of the second condenser and the flow path downstream of the third condenser and the evaporator;
And a second control section for controlling the closing means to close the shut-off means when the compressor stops operating. The method of claim 1,
Wherein the second control unit comprises:
And when the compressor is stopped, the flow path switching valve is switched to the second condenser side. The method of claim 1,
Internal temperature detecting means for detecting a temperature of the storage compartment;
And a third controller for controlling the refrigerant flow path of the flow path switching valve to be switched to the second condenser side when the detected temperature of the storage chamber is lower than a predetermined value and the refrigerant flows through the third condenser. , Refrigerator. The method of claim 1,
Internal temperature detecting means for detecting a temperature of the storage compartment;
After switching the flow path switching valve to the third condenser side, until the temperature detected by the internal temperature detecting means becomes a temperature higher than a predetermined value or until the compressor stops, And a fourth controller for controlling the refrigerant passage not to be switched to the third condenser side. The method of claim 1,
A machine room blower for radiating heat from a machine room accommodating the compressor;
And a fifth controller for controlling the rotational speed of the blower for the machine room when the refrigerant is flowing to the second condenser side as compared with when the refrigerant is flowing to the third condenser side. The method of claim 1,
According to the temperature which the temperature detection means in the said high temperature which detects the temperature in the said storage chamber detects,
Or according to the average temperature set value of the said storage room which the user adjusted by the storage room temperature control means,
Alternatively, in accordance with the number of times of switching of the flow path switching valve stored by the total flow path switching count storage means for storing the total number of times of switching of the flow path switching valve from the start of use of the refrigerator,
And a sixth control unit for changing a cycle time for switching the flow path switching valve.

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