JP2013155910A - Refrigerator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerator that has high energy saving performance while suppressing a refrigerant flowing sound by a refrigerant flow passage switching means.SOLUTION: A refrigerator including a compressor 24, a decompression means 45, a cooler 7, a plurality of storage compartments, partition parts 28, 29, and 30 partitioning off the plurality of storage compartments, and a dew condensation-proof pipe 43 heating the partition parts 28, 29, and 30 includes a heat dissipation means 42 in a refrigerant flow passage between the compressor 24 and the dew condensation-proof pipe 43, and also includes a first refrigerant circulation flow passage through which a refrigerant flows to the compressor 24, the heat dissipation means 42, the dew condensation-proof pipe 43, the decompression means 45, the cooler 7, and the compressor 24 in order, and a second refrigerant circulation flow passage through which a refrigerant flows to the compressor 24, the heat dissipation means 42, the decompression means 45, the cooler 7, and the compressor 24 in order, and there is provided a refrigerant flow passage switching means 101 for switching refrigerant flow passages of the first refrigerant circulation flow passage and the second refrigerant circulation flow passage in a place as a liquid phase area of the refrigerants flowing through the first refrigerant circulation flow passage and the second refrigerant circulation flow passage.

Description

  The present invention relates to a refrigerator.

  As background art of this technical field, there are JP-A-2004-92939 (Patent Document 1) and JP-A-2001-153493 (Patent Document 2).

  In Patent Document 1, a storage space in a freezing temperature zone, a storage space in a refrigeration temperature zone, a condensing pipe that is embedded in both side walls of the refrigerator and dissipates heat, and an opening that is disposed around the opening to prevent condensation. An edge condensing pipe, a bypass pipe for forming a bypass passage for flowing the refrigerant without going through the opening edge condensing pipe, and a three-way valve as a passage control means for adjusting the refrigerant flowing through the opening edge condensing pipe and the bypass pipe. A refrigerator-freezer provided is described (Patent Document 1, paragraph 0018, FIG. 2).

  Patent Document 2 includes a compressor, a main condenser (heat radiator), a sub-condenser (heat radiator), a capillary tube, an evaporator, and an electric switching valve. The upstream side (inlet side) of the main condenser is connected to the side by the refrigerant path, and the upstream side (inlet side) of the sub-condenser is connected to the refrigerant path branched from the downstream side (outlet side) of the main condenser, The downstream side (outlet side) of the main condenser is connected to the first inlet port of the electric switching valve by the refrigerant passage, and the downstream side (outlet side) of the sub-condenser is connected to the second switching port of the electric switching valve by the refrigerant passage. A refrigeration cycle apparatus for a refrigerator is described in which a capillary tube and an evaporator are connected in order to an outlet port of an electric switching valve connected to an inlet port, and an outlet side of the evaporator is connected to a suction side of a compressor by a refrigerant passage. (Patent Document 2, paragraphs 0016 and 0017, FIG. ).

JP 2004-92939 A JP 2001-153493 A

  In the refrigerator described in Patent Document 1, heat is prevented from flowing from the opening edge condensing pipe into the cabinet more than necessary by bypassing the opening edge condensing pipe as necessary.

  However, when the refrigerant discharged from the compressor passes through the condensing pipe and the opening edge condensing pipe, the refrigerant releases heat to the superheated gas region (gas phase region), gas-liquid two-phase region, and liquid phase region. And the phase changes in order. Basically, since the refrigerant reaches the liquid phase in the middle of the opening edge condensation pipe, when a three-way valve is installed between the condensation pipe and the condensation prevention pipe and heat is radiated through the opening edge condensation pipe, the state of the refrigerant inside the three-way valve Is a gas phase region or a gas-liquid two-phase region, and the refrigerant flow noise tends to increase when passing through the three-way valve, which may cause discomfort to the user. In Patent Document 1, the state of the refrigerant is not taken into consideration, and consideration is not given to the installation location of the switching means (three-way valve).

  Moreover, the refrigeration cycle apparatus described in Patent Document 2 has no specific description regarding the condenser and the sub-condenser. That is, there is no description that the sub-condenser is a dew condensation prevention pipe, and there is provided means for bypassing a part of the condenser as means for adjusting the heat radiation amount in the refrigeration cycle. Such means can be used for products that need to keep the temperature fluctuation in the tank within 1 ° C., such as a constant temperature culture tank, or when the temperature difference between the inside and outside of the refrigerator is extremely small. Although it is effective for adjusting the amount of heat dissipation, etc., in the normal cooling operation of the refrigerator (the storage room is cooled to the target temperature and the temperature difference between inside and outside the warehouse is large), even if the amount of heat radiation is reduced Energy saving performance is difficult to improve.

  This invention is made | formed in view of the above problems, and it aims at providing the refrigerator with high energy saving performance, suppressing the refrigerant | coolant flow noise by a refrigerant | coolant flow path switching means.

  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-described problems. For example, a compressor, a decompression means, a cooler, a plurality of storage chambers, and a partition that partitions the plurality of storage chambers. And a dew condensation prevention pipe for heating the partition part, wherein the refrigerant flow path is provided between the compressor and the dew condensation prevention pipe, and the refrigerant is supplied to the compressor and the heat radiation means. , The dew condensation prevention pipe, the decompression means, the cooler, and the first refrigerant circulation channel that flows in the order of the compressor, the refrigerant, the compressor, the heat dissipation means, the decompression means, the cooler, and the compression A second refrigerant circulation channel that flows in the order of the machine, and the first refrigerant circulation channel and the second refrigerant circulation channel that respectively flow through the first refrigerant circulation channel in the liquid phase region. A cooling circuit for switching between the second refrigerant circulation channel and the second refrigerant circulation channel. It provided with a flow path switching means.

  ADVANTAGE OF THE INVENTION According to this invention, the refrigerator with high energy saving performance can be provided, suppressing the refrigerant | coolant flow noise by a refrigerant | coolant flow path switching means.

It is a front view of the refrigerator in connection with Example 1 of this invention. It is AA sectional drawing of FIG. It is a front schematic diagram which shows arrangement | positioning etc. of the cold air duct of a refrigerator, a cold air outlet. It is a schematic diagram at the time of seeing the machine room interior structure of the refrigerator in connection with Example 1 from the back. It is a schematic diagram which shows the arrangement | positioning position of the side surface heat radiating pipe in the refrigerator of Example 1, and a dew condensation prevention pipe. 3 is a schematic cross-sectional view of the vicinity of a front surface portion of a partition wall in the refrigerator of Example 1. FIG. 3 is a schematic cross-sectional view of the vicinity of a front surface portion of a partition wall in the refrigerator of Example 1. FIG. 3 is a schematic cross-sectional view of the vicinity of a front surface portion of a partition wall in the refrigerator of Example 1. FIG. FIG. 3 is a diagram illustrating a configuration of a refrigeration cycle (refrigerant flow path) in the refrigerator according to the first embodiment. It is a figure explaining the relationship between the time ratio which switches a refrigerant | coolant flow path, and relative humidity in the refrigerator of Example 1. FIG. It is the figure which showed typically the state of the refrigerant | coolant inside piping from the compressor in the refrigerator of Example 1 to a capillary tube. It is the figure which showed typically the state of the refrigerant | coolant inside piping from the compressor in the refrigerator of Example 1 to a capillary tube. 3 is a time chart illustrating an example of a cooling operation in the refrigerator according to the first embodiment. It is a figure which shows the refrigerating cycle structure of the refrigerant | coolant flow path using the two-way valve instead of the three-way valve of FIG. It is a figure which shows the refrigerating cycle structure in the refrigerator of a comparative example. It is the figure which showed typically the state of the refrigerant | coolant inside piping from the compressor to the capillary tube in the refrigerator of a comparative example. It is the figure which showed typically the state of the refrigerant | coolant inside piping from the compressor to the capillary tube in the refrigerator of a comparative example. It is a Mollier (pressure-specific enthalpy) diagram at the time of the 3rd refrigerant | coolant flow path use in the refrigerator of a comparative example. It is a schematic diagram which shows the arrangement | positioning position of the side surface heat radiating pipe in the refrigerator of Example 2, a back surface heat radiating pipe, and a dew condensation prevention pipe. It is a figure which shows the refrigerating cycle structure in the refrigerator of Example 2. FIG. FIG. 6 is a diagram showing a refrigeration cycle configuration in the refrigerator of Example 3.

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

Example 1
Embodiment 1 of a refrigerator according to the present invention will be described with reference to FIGS.

  FIG. 1 is a front view of a refrigerator according to Embodiment 1 of the present invention. The refrigerator 1 of Example 1 is provided with the refrigerator compartment 2, the lower freezer compartment 5, and the vegetable compartment 6 from the top as a food storage compartment. Further, between the refrigerator compartment 2 and the lower freezer compartment 5, the ice making compartment 3 and the upper freezer compartment 4 are arranged on the left and right at the same height position. In the following, the freezing temperature zone 60 may be used as a general term for the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5, and the refrigerated temperature zone chamber 61 is used as a generic term for the refrigerating room 2 and the vegetable room 6. There is.

  The refrigerating room 2 is provided with doors 2a and 2b that are separated from each other on the front side, and the ice making room 3, the upper freezing room 4, the lower freezing room 5, and the vegetable room 6 are each a drawer type ice making. The room door 3a, the upper freezer compartment door 4a, the lower freezer compartment door 5a, and the vegetable compartment door 6a are provided.

  The interior of the refrigerator 1 is thermally insulated from the refrigerator compartment 2 and the freezing temperature zone 60 by the upper partition wall 28, and is insulated from the freezing temperature zone 60 and the vegetable compartment 6 by the lower partition wall 29. It is separated. Here, although the partition which heat-separates between the ice-making room 3, the upper stage freezing room 4, and the lower stage freezing room 5 is not provided, the sealing member provided in the circumferential shape on each inner surface of the doors 3a, 4a, and 5a. A freezing temperature zone chamber partition wall 30 that forms a magnetized surface and prevents leakage of air in the freezing temperature zone chamber 60 from the gaps of the doors 3a, 4a, and 5a to the outside of the refrigerator is provided.

  The refrigerator 1 also has a door sensor (not shown) that detects the open / closed state of each door, and an alarm that informs the user when it is determined that the door is open for a predetermined time or longer, for example, 1 minute ( And a temperature setting device (not shown) for setting the temperature of the refrigerator compartment 2 and the vegetable compartment 6 and the temperature setting of the freezing temperature zone 60. A door hinge that rotatably fixes the doors 2 a and 2 b to the refrigerator 1 is provided at the upper part of the refrigerator, and the door hinge is covered with a door hinge cover 110. At least one of the left and right door hinge covers 110 is provided with an outside air temperature sensor 111 and an outside air humidity sensor 112 that detect the temperature and humidity outside the warehouse. In the present embodiment, the outside air temperature sensor 111 and the outside air humidity sensor 112 are provided inside the door hinge cover 110 so that the temperature influence from the main body of the refrigerator 1 is not easily received, and the ambient temperature and the ambient humidity are detected. It is to do. In addition, the installation location of the outside air temperature sensor 111 and the outside air humidity sensor 112 is not limited to this, and the ambient temperature and the ambient humidity of the refrigerator 1 installation environment can be appropriately detected without being directly affected by the temperature from the refrigerator 1 body. Any place is acceptable.

  FIG. 2 is a cross-sectional view taken along the line AA of FIG. The inside and outside of the refrigerator 1 are separated by a heat insulating box 10 formed by filling a foam heat insulating material such as polyurethane foam between the outer box 1a and the inner box 1b. A vacuum heat insulating material 26 is mounted on the heat insulating box 10 of the refrigerator 1.

  A plurality of door pockets 32 are provided on the inner side of the doors 2a and 2b. The refrigerator compartment 2 is partitioned into a plurality of storage spaces in the vertical direction by a plurality of shelves 36. The upper freezer compartment 4, the lower freezer compartment 5, and the vegetable compartment 6 are provided with storage containers 4b, 5b, 6b that are pulled out integrally with the doors provided at the front of each chamber, respectively. The storage containers 4b, 5b, and 6b can be pulled out by placing the hand on (not shown) and pulling it out to the front side. Similarly, the ice making chamber 3 shown in FIG. 1 is provided with a storage container (reference numeral 3b in FIG. 2) that is pulled out integrally with the ice making chamber door 3a, and a handle (not shown) of the ice making chamber door 3a is hooked. The container 3b can be pulled out by pulling it out to the front side. The upper freezer compartment 4 is configured to be used as a quick freezer compartment. In order to improve the quick freezing performance, the storage container 4b of the upper freezer compartment 4 is provided with an aluminum tray (not shown) to improve the freezing speed.

  In the refrigerator 1, a cooler storage chamber 8 is defined in a substantially back portion of the freezing temperature zone chamber 60. The cooler 7 is disposed substantially at the back of the lower freezer compartment 5 and is provided in the cooler storage chamber 8. The air cooled by exchanging heat with the cooler 7 is sent to the refrigerating room 2 through the refrigerating room duct 11 by the internal fan 9 provided above the cooler 7, and the vegetable room duct (not shown). ) To the vegetable compartment 6. Similarly, the air cooled by the cooler 7 is sent to the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5 through the freezer duct 13. The air blowing to each room is controlled by opening and closing the refrigerator compartment damper 50, the vegetable compartment damper 51 (see FIG. 3), and the freezer compartment damper 52 in conjunction with a temperature sensor provided in each compartment to be described later. In addition, when the vegetable compartment 6 becomes too low temperature, the vegetable compartment 6 is heated by supplying with electricity the vegetable compartment electric heater (not shown) provided in the vegetable compartment 6.

  The refrigerator 1 has a cooler temperature sensor 35 at the upper left of the cooler 7 when viewed from the front, a refrigerator temperature sensor 33 at the refrigerator compartment 2, a vegetable compartment temperature sensor 33a at the vegetable compartment 6, and a freezer compartment temperature sensor at the lower freezer compartment 5. 34 respectively. The cooler temperature sensor 35, the refrigerator temperature sensor 33, the vegetable room temperature sensor 33a, and the freezer temperature sensor 34 are respectively the temperature of the cooler 7, the temperature of the refrigerator room 2, the temperature of the vegetable room 6, and the temperature of the lower freezer room 5. It is configured to detect the temperature. Further, as described above, the refrigerator 1 is also provided with an outside air temperature sensor 111 and an outside air humidity sensor 112 that detect the temperature outside the refrigerator.

  The refrigerator 1 has a control board 31 on which a CPU, a memory such as a ROM and a RAM, an interface circuit, and the like are mounted on the upper surface of the ceiling wall. The control board 31 detects the open / closed state of each door, as described above, the outside air temperature sensor 111, the outside air humidity sensor 112, the cooler temperature sensor 35, the refrigerating room temperature sensor 33, the vegetable room temperature sensor 33a, the freezer room temperature sensor 34, and the like. It is connected to the door sensor, temperature setter, etc. described above. Based on these output values and a program recorded in advance in the ROM, the CPU described above controls the ON / OFF of the compressor 24, the control of a three-way valve 101 (see FIG. 4) described later, and the refrigerator damper 50. Control of each actuator (not shown) for individually driving the vegetable compartment damper 51 and the freezer compartment damper 52, ON / OFF control and rotational speed control of the internal fan 9, and notification of the above-described door open state Controls alarm ON / OFF, etc.

  In addition, a defrost heater 22 that heats frost adhering to the cooler 7 during the defrosting operation is installed below the cooler 7. The defrosted water generated by the defrosting flows into the eaves 23 provided at the lower part of the cooler storage chamber 8, and then reaches the evaporating dish 21 disposed in the machine chamber 19 described later via the drain pipe 27. It evaporates due to the heat from the external radiator 41 (see FIG. 4) and the compressor 24.

  FIG. 3 is a schematic front view showing the arrangement of the cold air duct and the cold air outlet in the warehouse. When the refrigerator compartment damper 50 is in the open state, the cold air exchanged by the cooler 7 is boosted by the internal fan 9 and sent to the refrigerator compartment 2 from the outlets 2c provided in multiple stages via the refrigerator compartment duct 11. . The cold air that has cooled the refrigerator compartment 2 returns to the cooler housing chamber 8 through the refrigerator compartment return duct 16 from the refrigerator inlet air return port 2d formed in the lower back of the refrigerator compartment 2, and is cooled again by the cooler 7. Is done.

  When the vegetable compartment damper 51 is in the open state, the cold air exchanged by the cooler 7 is pressurized by the internal fan 9 and provided at the upper right side of the vegetable compartment 6 via the vegetable compartment duct (not shown). The vegetable room 6 is cooled by flowing into the vegetable room 6 from the vegetable room outlet 6c. The cold air that has cooled the vegetable compartment 6 returns from the vegetable compartment return port 6d provided at the lower left front of the lower partition wall 29 to the cooler storage compartment 8 via the vegetable compartment return duct 18 (see FIG. 2). Cooled by the cooler 7.

  When the freezer damper 52 is in the open state, the cold air heat-exchanged by the cooler 7 is boosted by the internal fan 9 and passes through the freezer duct 13 from the outlets 3c, 4c and 5c, respectively. The air is sent to the upper freezer compartment 4 and the lower freezer compartment 5. Then, the cold air that has cooled the ice making chamber 3, the upper freezing chamber 4, and the lower freezing chamber 5 returns to the cooler storage chamber 8 from the freezer return port 17 (see FIG. 2), and is cooled again by the cooler 7. Here, the number of outlets 3c, 4c, and 5c of the freezing temperature zone chamber 60 is one in the ice making chamber 3, one in the upper freezing chamber 4, and five in the lower freezing chamber 5, respectively. It is not a thing.

  FIG. 4 is a schematic diagram of the machine room configuration of the refrigerator according to the first embodiment when viewed from the back. As shown in FIG. 2, the refrigerator 1 includes a machine room 19 on the outside of the heat insulating box 10, on the lower back of the vegetable room 6 of the refrigerator 1 and on the lower part of the cooler storage room 8. In the machine room 19, a three-way valve 101, a compressor 24, an outside fan 41 a, and an outside heat radiator 41, which will be described later, are disposed in order from the left, and the lower part of the drain pipe 27 is disposed above the compressor 24. Is provided with an evaporating dish 21. The machine room 19 is provided with machine room openings 19a and 19b on both side surfaces so that outside air can enter and exit from the machine room openings 19a and 19b. During the cooling operation, the high-temperature compressor 24 and the external radiator 41 radiate heat by external air taken from the machine room opening 19a by driving the external fan 41a. The air heated by the heat radiation is discharged outside from the machine room opening 19b. The evaporating dish 21 stores water dripped from the drain pipe 27 after defrosting, and this water is vaporized by the heat in the machine room 19 and discharged to the outside air from the machine room opening 19b.

  FIG. 5 is a diagram illustrating the arrangement positions of the side heat radiation pipe 42 and the dew condensation prevention pipe 43 in the refrigerator according to the first embodiment. The refrigerator 1 according to the present embodiment has a side heat radiating pipe 42, which will be described later, between the outer box 1a and the inner box 1b on the side of the refrigerator 1 indicated by a dotted line in FIG. It arrange | positions so that it may contact | connect. The outer box 1a is made of a steel plate and can radiate heat well from the outer surface of the outer box 1a to the outside air. Further, a dew condensation prevention pipe 43 indicated by a one-dot chain line in FIG. 5 is disposed in front of the upper partition wall 28, the lower partition wall 29, and the freezing temperature zone partition wall 30.

  Details of the vicinity of the condensation prevention pipe 43 are shown in FIGS. 6a, 6b, and 6c. 6a is a schematic cross-sectional view of the vicinity of the front surface portion of the partition wall in the refrigerator of the first embodiment, and schematically illustrates a cross section of the front surface portion of the freezing temperature zone partition wall 30 in the vicinity of the dew condensation prevention pipe 43 of the first embodiment. FIG. 3 is an enlarged view of FIG. 2. A dew condensation prevention pipe 43 through which the high-temperature refrigerant discharged from the compressor 24 flows is provided inside the refrigeration temperature zone chamber partition wall 30, and the dew condensation prevention pipe 43 is a partition cover provided on the front surface of the refrigeration temperature zone chamber partition wall 30. It is provided in the vicinity of 30a. In addition, the partition cover 30a of the refrigerator 1 according to the present embodiment is made of a steel plate in order to increase thermal conductivity.

  The surface of the partition cover 30a and the ambient air are cooled by the refrigeration temperature zone chamber 60 at about -18 ° C. where the refrigeration temperature zone compartment partition wall 30 is provided, so that the humidity around the refrigerator is not high. In such a case, condensation may occur on the surface of the partition cover 30a due to moisture in the air near the partition cover 30a. In order to avoid this dew condensation, a high-temperature refrigerant is caused to flow through the dew condensation prevention pipe 43, heat is exchanged between the partition cover 30a and the refrigerant, and the heat flow indicated by 93 in the figure (the flow of heat transmitted from the dew condensation prevention pipe 43 to the outside) ) Is heating the partition cover 30a. 6B is a cross section of the front partition wall 28 in the vicinity of the dew condensation prevention pipe 43 of the refrigerator according to the first embodiment, and FIG. 6C is a diagram of the lower partition wall 29 in the vicinity of the dew condensation prevention pipe 43 of the refrigerator according to the first embodiment. FIG. 3 is an enlarged view of FIG. 2 schematically showing a cross section in the vicinity of the front surface portion. The upper partition wall 28 and the lower partition wall 29 have the same configuration as the refrigeration temperature zone partition wall 30 shown in FIG. 6a, and a partition cover 28a provided inside the partition walls 28 and 29 and on the front surface portion. , 29a, a dew condensation prevention pipe 43 is provided to suppress dew condensation on the partition covers 28a, 29a.

  On the other hand, considering that heat exchange occurs when there is a temperature difference between adjacent objects and substances, the refrigerant in the dew condensation prevention pipe 43 provided on each partition wall is adjacent to each partition wall 28, 29, 30. Heat exchange is also performed with the air in the refrigerator compartment 2, the freezing temperature zone 60, and the vegetable compartment 6. That is, the dew condensation prevention pipe 43 causes the heat in the refrigerator compartment 2, the freezing temperature zone room 60, and the vegetable room 6 to flow in the heat flow indicated by 94 in the figure (heat flow transmitted from the dew condensation prevention pipe 43 to the storage room side), and Heat is exchanged with the refrigerant in the dew condensation prevention pipe 43 to heat the interior. As a result, it is necessary to cool again the heat that has flowed into the cabinet by the dew condensation prevention pipe 43, resulting in a decrease in energy saving performance.

  Therefore, in the refrigerator 1 of the present embodiment, the refrigeration cycle is configured so that the heating amount by the dew condensation prevention pipe 43 can be adjusted. FIG. 7 is a diagram illustrating the configuration of the refrigeration cycle (refrigerant flow path) of the refrigerator according to the first embodiment. The refrigerator 1 of the present embodiment includes a compressor 24, an external radiator 41, a side heat radiating pipe 42, a dew condensation preventing pipe 43, a dryer 44, a capillary tube 45, a cooler 7, and a gas-liquid separator 46, and a refrigerant branch. The part 100 and the three-way valve 101 for controlling the refrigerant flow path are provided, and these are connected by connecting pipes connecting members constituting the refrigeration cycle indicated by reference numerals 72 to 82. Hereinafter, the connection pipes 72 to 81 may be collectively referred to as the connection pipe 71.

  Note that the refrigerator 1 of the present embodiment uses isobutane as a refrigerant.

  The refrigerant branch part 100 is a member that is connected to the three connection pipes 74, 75, and 76, and always connects the three connection pipes 74, 75, and 76 connected to the refrigerant branch part 100. The three-way valve 101 includes two inlets indicated by 101i_A and 101i_B and an outlet indicated by 101o, and is a member that allows any one of the two inlets 101i_A and 101i_B to communicate with the outlet 101o. . Furthermore, in the three-way valve 101 of the present embodiment, the outlet 101o is a member that can close the refrigerant flow path in a state where it does not communicate with any of the inlets 101i_A and 101i_B. In the following, the state in which the inlet 101i_A and the outlet 101o are in communication are in the A state, the state in which the inlet 101i_B and the outlet 101o are in communication are in the B state, and neither the inlet 101i_A or 101i_B is in communication. Let the state be the C state.

  Next, the connection relationship of each component will be described. The connection pipe 72 connects the discharge port of the compressor 24 and the external heat radiator 41, the connection pipe 73 connects the external heat radiator 41 and the side heat radiating pipe 42, and the connection pipe 74 connects the side heat radiating pipe 42 and the refrigerant branch portion 100. Are connected to each other. In addition, the refrigerant branching portion 100 is connected to a connection pipe 75 and a connection pipe 76.

  The connection pipe 75 connects the refrigerant branch part 100 and the dew condensation prevention pipe 43. The dew condensation prevention pipe 43 is connected to the inflow port 101i_A of the three-way valve 101 at the other end by a connection pipe 77. The other end of the connection pipe 76 connected to the refrigerant branching unit 100 is connected to the inlet 101 i_B of the three-way valve 101.

  The connection pipe 78 connects the outlet 101o of the three-way valve 101 and the dryer 44, the connection pipe 79 connects the dryer 44 and the capillary tube 45, the connection pipe 80 connects the capillary tube 45 and the cooler 7, and the connection pipe 81 The cooling pipe 7 and the gas-liquid separator 46 are connected, and the connection pipe 82 connects the gas-liquid separator 46 and the compressor 24.

  The above is the refrigeration cycle configuration of the refrigerator 1 of the present embodiment. Next, the first refrigerant circulation passage A in which the three-way valve 101 is formed with the inflow port 101i_A and the outflow port 101o in communication, that is, the A state will be described.

  The refrigerant that has become high temperature and high pressure by the compressor 24 flows into the external heat radiator 41 and the side surface heat radiation pipe 42 via the connection pipes 72 and 73 and is radiated by these. Thereafter, the refrigerant flows into the refrigerant branch portion 100 through the connection pipe 74. Here, since the three-way valve 101 is in communication between the inlet 101i_A and the outlet 101o and the connection pipe 76 cannot pass through, the refrigerant that has flowed into the refrigerant branch portion 100 flows into the dew condensation prevention pipe 43 via the connection pipe 75. The dew condensation prevention pipe 43 also radiates heat. The heat is applied to the partition covers 28a, 29a, 30a (see FIGS. 6a, 6b, and 6c), and then the refrigerant flows into the three-way valve 101 through the connection pipe 77.

  In the three-way valve 101, since the inlet 101i_A and the outlet 101o are communicated with each other, the refrigerant flows into the dryer 44 and the capillary tube 45 through the connection pipes 78 and 79, and the pressure is reduced in the capillary tube 45. The decompressed refrigerant flows into the cooler 7 through the connection pipe 80, and evaporates and absorbs heat in the cooler 7. The refrigerant that has absorbed heat returns to the compressor 24 via the connection pipe 81, the gas-liquid separator 46, and the connection pipe 82.

  Next, the second refrigerant circulation passage B in which the three-way valve 101 is formed with the inflow port 101i_B and the outflow port 101o in communication, that is, in the B state will be described.

  Similarly to the first refrigerant circulation flow path A, the refrigerant that has become high temperature and high pressure by the compressor 24 flows into the refrigerant branching portion 100 through each connection pipe 71 while radiating heat through the external radiator 41 and the side surface heat radiating pipe 42. . Here, since the three-way valve 101 communicates the inflow port 101i_B and the outflow port 101o, the refrigerant that has flowed into the refrigerant branch portion 100 flows into the three-way valve 101 via the connection pipe 76. Thereafter, similarly to the first refrigerant circulation flow path A, the flow returns to the compressor 24 while flowing into the dryer 44, the capillary tube 45, the cooler 7, and the gas-liquid separator 46 via the connection pipes 78 to 82.

  As described above, the refrigerator 1 according to the present embodiment includes the flow path for flowing the refrigerant through the dew condensation prevention pipe 43 and the flow path for not flowing the refrigerant, that is, the state flowing through the first refrigerant circulation path A and the second refrigerant circulation flow. The state which flows through the path | route B is provided, and these can be switched. Thereby, the heating amount of the dew condensation prevention pipe 43 is adjusted.

  As described above, the heat radiation by the dew condensation prevention pipe 43 is effective in suppressing the dew condensation of the partition covers 28a, 29a, and 30a (see FIGS. 6a, 6b, and 6c), but it heats the inside of the cabinet. This leads to a decrease in energy saving performance. Therefore, when the ambient environment in which condensation is likely to occur is high temperature and high humidity, the heating rate of the condensation prevention pipe 43 is increased by increasing the proportion of time in which the state flowing through the first refrigerant circulation passage is used. When the ambient environment where condensation is unlikely to occur is low temperature and low humidity, the heating rate of the condensation prevention pipe 43 is reduced by increasing the proportion of time using the state flowing through the second refrigerant circulation passage B. That is, the partition cover 30a is heated so that no condensation occurs or grows by the first refrigerant circulation flow path A, but the refrigerant is switched to the second refrigerant circulation flow path B so that it is not heated further. Energy saving performance is improved while preventing condensation.

  FIG. 8 is a diagram for explaining the relationship between the relative humidity and the time ratio at which the first refrigerant circulation channel and the second refrigerant circulation channel are switched by the three-way valve 101 in the refrigerator according to the first embodiment. In the refrigerator 1 of the present embodiment, the first refrigerant circulation channel A and the second refrigerant circulation channel B are determined by the temperature and humidity around the refrigerator obtained by the outside temperature sensor 111 and the outside humidity sensor 112 described above. Is switched.

  FIG. 8 shows the relationship of the time ratio when the refrigerant flow path is set to the first refrigerant circulation flow path A side with respect to the ambient humidity detected by the outside air humidity sensor 112 in the case of a certain ambient temperature detected by the outside air temperature sensor 111. ing. The horizontal axis represents the relative humidity, and the vertical axis represents the heating rate of the dew condensation prevention pipe 43, that is, the rate of time during which the refrigerant flow path is on the first refrigerant circulation flow path A side. For example, in the case of RH2 where the relative humidity is high, there is a high possibility of dew condensation on the surface of each partition cover 28a, 29a, 30a. Therefore, the ratio of time for flowing the refrigerant with the three-way valve 101 in the A state (tA2) is increased. The ratio (tB2) of flowing the refrigerant in the B state is shortened. On the other hand, in the case of RH1 where the humidity is low, the possibility of condensation on the surface of each partition cover is low. Thus, it is preferable to increase the ratio (tB1) of the flow time of the refrigerant. In actual cooling operation, the switching time on the first refrigerant circulation channel A side and the second refrigerant circulation channel B side in accordance with the temperature and humidity is determined in advance, and when the compressor 24 is ON, the time Accordingly, the three-way valve 101 is operated by switching between the A state and the B state. For example, in the refrigerator 1 according to the present embodiment, the A state is switched to 10 minutes when the ambient air is 30 ° C. and the relative humidity is 50%, and the B state is switched to 20 minutes when the ambient temperature is 30 ° C. relative humidity. At 70%, the A state is switched in 20 minutes and the B state is switched in 10 minutes.

  As described above, the refrigerator 1 according to the present embodiment heats the front surfaces of the upper partition wall 28, the lower partition wall 29, and the freezing temperature zone chamber partition wall 30 in order to improve energy saving performance while suppressing condensation on the wall surface. A dew condensation prevention pipe 43 for preventing dew condensation, a state of flowing through the first refrigerant circulation channel A for flowing the refrigerant through the dew condensation prevention pipe 43, and a refrigeration other than the dew condensation prevention pipe 43 by bypassing the dew condensation prevention pipe 43. A state is provided in which the refrigerant flows through the second refrigerant circulation passage B that causes the refrigerant to flow through the cycle constituent member, and the amount of heating of the dew condensation prevention pipe 43 is adjusted by switching between the two refrigerant passages.

  In addition, as shown in FIG. 7, condensation prevention is achieved in which the refrigerant in the liquid phase flows through the three-way valve 101 which is a refrigerant flow path switching means for switching between the first refrigerant circulation path and the second refrigerant circulation path. The pipe 43 is provided downstream of the refrigerant flow path. Thereby, a refrigerator with high energy saving performance can be obtained while suppressing an increase in refrigerant flow noise caused by the refrigerant flow switching means. The reason why an increase in refrigerant flow noise can be suppressed will be described below.

  9a and 9b are diagrams schematically showing the refrigerant state inside the pipe from the discharge port of the compressor 24 to the capillary tube 45 of the first embodiment, and FIG. 9a is a diagram showing the first refrigerant circulation channel A and FIG. 9b. Represents the state of the second refrigerant circulation passage B. In FIG. 9a, the reference numeral 91 is a gas refrigerant, the reference numeral 92 is a liquid refrigerant, the gas phase region of the gas refrigerant 91 only is the section ab, the gas-liquid two-phase area where the gas refrigerant 91 and the liquid refrigerant 92 are mixed is the section bc, and the liquid refrigerant. The liquid phase region of only 92 is denoted as section cd. The section ae is from the discharge of the compressor 24 including the external radiator 41 to the outflow portion of the external radiator 41, and the section ef is from the outflow portion of the external radiator 41 including the side surface heat radiating pipe 42 to the refrigerant branching section 100. fg represents from the refrigerant branching portion 100 including the condensation prevention pipe 43 to the three-way valve 101, and a section gd represents from the three-way valve 101 including the dryer 44 to the capillary tube 45. In FIG. 9 b, the condensation branch pipe 100 bypasses the dew condensation prevention pipe 43, flows through the connection pipe 76, and flows to the three-way valve 101.

  The gas refrigerant compressed to high temperature and high pressure by the compressor 24 releases heat in the order of the external radiator 41, the side surface heat radiating pipe 42, and the dew condensation preventing pipe 43 in order, and the gas phase region and section indicated by the section ab The gas-liquid two-phase region during phase change indicated by bc, the liquid phase region indicated by section cd, and the state of the refrigerant change. Since the three-way valve 101 for switching the first refrigerant circulation passage A and the second refrigerant circulation passage B is provided between the dew condensation prevention pipe 43 and the dryer 44, the three-way valve 101 is indicated by g in FIGS. 9a and 9b. In these positions, the liquid refrigerant of only the liquid refrigerant 92 flows on both the first refrigerant circulation channel A side and the second refrigerant circulation channel B side.

  Here, the inside of the three-way valve 101 that controls the refrigerant generally has a flow path having a smaller diameter than the front and rear connecting pipes 77 and 78 so that the valve can be easily opened and closed. Under constant density conditions, the flow rate of the refrigerant increases due to the reduction in the cross-sectional area of the refrigerant flow path, and as a result, the refrigerant flow noise increases. At this time, the density of the liquid refrigerant 92 is higher than that of the gas refrigerant 91. For example, in the case of isobutane, the liquid is 50 to 100 times that of the gas. It flows at 1/50 to 1/100 times the low speed. Therefore, even if the liquid refrigerant 92 has a higher flow rate due to the reduction of the refrigerant flow path than the gas refrigerant 91, the liquid refrigerant 92 is sufficiently slow compared to the gas refrigerant 91 and the refrigerant flow noise is small. Accordingly, the three-way valve 101 in the refrigerator 1 according to the present embodiment is in a position for controlling the liquid refrigerant 92 having a slower flow rate than the gas refrigerant 91, thereby suppressing an increase in refrigerant flow noise.

  Further, since the liquid refrigerant 92 is controlled on both the first refrigerant circulation channel A side shown in FIG. 9a and the second refrigerant circulation channel B side shown in FIG. In addition, it is considered that the change of the refrigerant flow sound accompanying the refrigerant flow switching is small. Therefore, by controlling the refrigerant in the liquid phase region with the three-way valve 101, it is possible to obtain a refrigerator with high energy-saving performance that suppresses the rise of the refrigerant flow noise caused by the refrigerant flow switching means and suppresses the internal heating by the condensation prevention pipe 43. It is done.

  Furthermore, in the refrigerator 1 of this embodiment, the switching time of the A state and the B state of the three-way valve 101 is set to a relatively long time of 3 seconds. When the time required for switching the three-way valve 101 is short, for example, within 0.5 seconds, the pressure before and after the three-way valve 101 changes abruptly, so the load on the three-way valve 101 is large. In addition, for example, the liquid refrigerant 92 exists in the gas-liquid two-phase region or the liquid-phase region, so that a water hammer may be generated. On the other hand, when the switching time of the valve is lengthened, for example, when the three-way valve 101 is switched from the A state to the B state, the refrigerant flow path of the inlet 101i_A is gradually reduced and the inlet 101i_B is gradually enlarged. Since a refrigerant flow path having a very small cross-sectional area exists, there is a possibility that a large flow rate of the refrigerant flows due to an increase in the flow velocity. Therefore, in the present embodiment, the refrigerant flow rate through the three-way valve 101 is the liquid refrigerant 92, so that the refrigerant flow rate can be controlled at a lower speed than that of the gas refrigerant 91. Therefore, the valve switching time can be extended as compared with the case where the refrigerant in the gas region or the two-phase region is controlled. Therefore, since the state of the three-way valve 101 is switched without instantaneously closing the inlets 101i_A and 101i_B of the three-way valve 101, the load on the water hammer and the three-way valve 101 can be suppressed.

  Moreover, in the refrigerator 1 of this Embodiment, the energy saving performance is improved even when the compressor is stopped. FIG. 10 is a time chart illustrating an example of the cooling operation of the refrigerator according to the first embodiment. The cooling operation in a stable state after the inside of the chamber reaches a predetermined temperature is a refrigeration operation for cooling the refrigeration chamber 2, a refrigeration operation for cooling the refrigeration temperature zone chamber 60, and has grown into a cooler with the compressor stopped. Based on an operation pattern consisting of a frost cooling operation in which the refrigeration temperature zone chamber is cooled by frost, these operations are repeated as long as the ambient temperature is not changed or food is not charged. Specifically, the compressor 24 is turned on when the temperature rises to the freezer compartment temperature TF1 while the compressor is stopped, and the refrigeration operation is performed. When the temperature of the refrigerator compartment decreases and reaches the temperature TR, the refrigerator operation is terminated, and the refrigerator operation is continued until the temperature of the freezer compartment reaches TF2.

  Next, the operation of the three-way valve 101 will be described in relation to the compressor 24. In the refrigerator of the present embodiment, the method for cooling the vegetable compartment 6 is not shown because it is not directly related to the operation of the three-way valve 101.

  When the compressor 24 is in operation, as shown in FIG. 8, the switching time of the A state and the B state is determined in advance according to the temperature and humidity, and the three-way valve 101 is switched accordingly. In the cooling operation shown in FIG. 10, the three-way valve 101 is fixed in the A state before the compressor 24 stops. This is because the temperature of the dew condensation prevention pipe 43 tends to be low when the compressor 24 is stopped. Therefore, before the compressor 24 is stopped, the dew condensation prevention pipe 43 increases the surface temperature of the partition covers 28a, 29a, 30a to prevent dew condensation. Because. Similarly, in order to increase the surface temperature of the partition covers 28a, 29a, and 30a that have become low temperature while the compressor 24 is stopped, the three-way valve 101 is in the A state immediately after the compressor 24 is started.

  When the compressor 24 is stopped, the refrigerant from the heat dissipation side, i.e., the external heat radiator 41, the side heat radiation pipe 42, the dew condensation prevention pipe 43, the dryer 44, and the connection pipes 71 to 79 is the heat absorption side, i.e., the cooler. 7. Since the pressure is higher than that of the refrigerant up to the gas-liquid separator 46 and the connecting pipes 80 to 82, the high-temperature refrigerant on the heat radiation side flows into the cooler side due to the pressure difference when the refrigerant flow path is not controlled. . Therefore, the temperature of the cooler 7 rises, and it becomes necessary to cool the cooler 7 whose temperature has risen when the next compressor 24 is driven, leading to a reduction in energy saving performance. Therefore, in the refrigerator 1 of the present embodiment, when the compressor is stopped, the three-way valve 101 is in the C state (the state where it does not communicate with any one of the inlets 101i_A and 101i_B) to close the refrigerant flow path, and this refrigerant The flow of energy is stopped and energy saving performance is improved. Further, in the refrigerator 1 of the present embodiment, the internal fan 9 is turned on, the refrigerator compartment damper 50 is opened, the freezer compartment damper 52 is closed, and cold air is generated by the frost grown on the cooler 7 to produce the refrigerator compartment 2. Operation (frost cooling operation) is provided. That is, the frost cooling operation is performed while the compressor shown in FIG. 10 is stopped. Here, when the three-way valve 101 is set to the C state while the compressor 24 is stopped, the temperature rise of the frost grown on the cooler 7 and the cooler 7 can be suppressed as described above, and the refrigerator compartment in the frost cooling operation. The cooling efficiency of No. 2 increases, contributing to energy saving performance improvement.

  As described above, the three-way valve 101 of the present embodiment has the three-way valve 101 in the C state while the compressor 24 is stopped, as well as the switching control of the first refrigerant circulation channel A side and the second refrigerant circulation channel B side. In addition, control for stopping the flow of the high-temperature refrigerant on the upstream side of the refrigerant flow path from the three-way valve 101 is also performed. This suppresses heating in the cabinet by the dew condensation prevention pipe 43 and also suppresses heating of the cooler 7 by the high-temperature refrigerant, so that a refrigerator with higher energy saving performance can be obtained.

  In the refrigerator 1 of the present embodiment, the three-way valve 101 is used as a means for switching between the first refrigerant circulation channel A side and the second refrigerant circulation channel B side. Absent. FIG. 11 is a diagram showing a refrigerant cycle refrigeration cycle configuration using a two-way valve instead of the three-way valve of FIG. The two-way valve 102A is provided between the condensation prevention pipe 43 and the refrigerant branching portion 200, and the three-way valve 102B is provided between the branching portion 100 and the refrigerant branching portion 200, bypassing the condensation prevention pipe 43. It is a member that can be switched between opening and closing. By configuring the refrigerant flow path as shown in FIG. 11, a refrigerant flow path equivalent to that in FIG. 7 can be configured. Specifically, the two-way valve 102A is opened and the two-way valve 102B is closed, so that it is equivalent to the state A of the three-way valve 101, that is, the first refrigerant circulation passage A side is configured. By setting 102A to the closed state and the two-way valve 102B to the open state, the same state as the B state, that is, the first refrigerant circulation channel B side is configured. Moreover, it can also be made equivalent to the C state of the three-way valve 101 by making the two-way valves 102A and 102B closed. Since the two-way valve 102A is provided on the downstream side of the dew condensation prevention pipe 43, the refrigerant in the liquid phase region flows. In addition, since the two-way valve 102B is on the downstream side of the side heat radiation pipe 42 that is the terminal heat radiation part on the second refrigerant circulation channel B side through which the refrigerant passes through the two-way valve 102B, this is also the liquid phase region. The refrigerant flows. Thereby, like the refrigerator 1 of Example 1 shown in FIG. 7, the two-way valve 102A and the two-way valve 102B can control the liquid refrigerant 92. That is, a refrigerator with high energy saving performance can be obtained while suppressing an increase in refrigerant flow noise.

(Comparative example)
Next, the structure of the refrigerator (refer patent document 1) of a comparative example is demonstrated. The refrigerant flow path configuration of the refrigerator 1 of this comparative example will be described with reference to FIGS. 12, 13a, and 13b. In addition, about the member same as Example 1, the same code | symbol is attached | subjected and description is abbreviate | omitted.

  FIG. 12 is a diagram showing a refrigeration cycle configuration in the refrigerator of the comparative example. The refrigerant flow path shown in FIG. 12 includes a three-way valve 201 instead of the refrigerant branch part 100 of FIG. 7 and includes a refrigerant branch part 200 instead of the three-way valve 101. The three-way valve 201 is a member having an inlet port 201i and two outlet ports 201o_A and 201o_B. The inlet 201i and the outlet port 201o_A of the three-way valve 201 are in the D state when in communication with each other. The inflow port 201i and the outflow port 201o_B are in the E state when in communication with each other, forming a fourth refrigerant circulation channel. Further, in the three-way valve 201 of the comparative example, the inflow port 201i is a member having an F state that does not communicate with any of the outflow ports 201i_A and 201i_B. In addition, the refrigerator 1 of this comparative example also uses isobutane as a refrigerant as in the first embodiment.

  FIG. 13 a is a diagram schematically showing the refrigerant state inside the pipe from the compressor 24 discharge port of the third refrigerant circulation passage to the capillary tube 45 related to the refrigerator 1 of the comparative example. When the three-way valve 201 for switching the third refrigerant circulation channel and the fourth refrigerant circulation channel is provided at a position f in the figure, which is upstream of the dew condensation prevention pipe 43, the refrigerant at the position f is in a gas-liquid two-phase region. Therefore, the three-way valve 201 controls the mixed refrigerant of the gas refrigerant 91 and the liquid refrigerant 92.

  Similar to the three-way valve 101 described above, the pipe inside the three-way valve 201 is generally different in diameter from the front and rear connection pipes 74 and 75, and when passing through the three-way valve 201, the refrigerant flow noise is generated due to the reduction of the refrigerant flow path. growing. Here, as described in the first embodiment, the gas refrigerant 91 has a lower density than the liquid refrigerant 92 and thus has a high flow rate. When the gas refrigerant 91 passes through the three-way valve, the flow rate is further reduced due to the reduction of the refrigerant flow path. It is considered that a large refrigerant flow noise is generated.

  Further, when switching between the D state and the E state of the three-way valve 201, the outflow port 201o_A or the outflow port 201o_B of the three-way valve 201 that is in the communication state is closed. At this time, when the switching of the three-way valve 201 is performed in a short time, the pressure changes abruptly and the load on the three-way valve 201 is large, and the liquid refrigerant 92 exists in the gas-liquid two-phase region. It is also conceivable that a sound is generated due to the impact. On the other hand, when the switching time of the three-way valve 201 is increased, for example, when switching from the D state to the E state, the outlet 201o_A in the three-way valve 201 in which the gas-liquid two-phase refrigerant including the gas refrigerant 91 flows gradually Since the refrigerant closes and gradually expands the outlet 201o_B, the refrigerant passes through the narrow refrigerant flow path and the flow velocity of the gas refrigerant 91 becomes very fast, so that a large refrigerant flow noise is likely to occur. Therefore, it is difficult to suppress the refrigerant flow noise and the load on the valve when the three-way valve 201 is switched.

  In the refrigerator 1 of the comparative example, the state of the refrigerant passing through the three-way valve 201 is different between the third refrigerant circulation channel D side and the fourth refrigerant circulation channel E side. FIG. 13b is a diagram schematically showing the state of the refrigerant in the condenser on the fourth refrigerant circulation passage E side in FIG. Since the fourth refrigerant circulation channel dissipates heat only by the external radiator 41 and the side surface heat radiation pipe 42, the most downstream heat radiation means is the side surface heat radiation pipe 42, and basically the refrigerant reaches the liquid phase region up to here. ing. Therefore, the refrigerant in the liquid phase flows through the three-way valve 201 provided at the position f. That is, when the three-way valve 201 is provided at the position f in FIG. 13, the gas-liquid two-phase region refrigerant flows in the third refrigerant circulation channel, and the liquid-phase region refrigerant flows in the fourth refrigerant circulation channel. The state of the refrigerant passing through the three-way valve 201 is changed by switching the flow path. Therefore, it is considered that the refrigerant flow noise also changes by switching the flow path. Humans are more likely to notice sound when the volume level or tone changes abruptly than a steady sound, and may feel uncomfortable with the change in refrigerant flow noise during refrigerant switching. Furthermore, when switching from the fourth refrigerant circulation channel to the third refrigerant circulation channel, a part of the refrigerant flowing through the three-way valve 201 changes from the liquid refrigerant 92 to the gas refrigerant 91, and thus a boiling sound is generated. It is also possible to do.

  As a method for suppressing an increase in refrigerant flow noise caused by the three-way valve 201 in the refrigerator 1 of the comparative example, it is conceivable to increase the amount of refrigerant enclosed in the refrigerant flow path. When the amount of refrigerant filled is increased, generally the liquid refrigerant 92 having a high density is increased, and the region of the liquid phase region is increased. That is, the position of the line c in FIG. 13a is shifted to the right. Therefore, the ratio of the liquid refrigerant 92 when passing through the three-way valve 201 is increased, and an increase in refrigerant flow noise caused by the three-way valve 201 can be suppressed.

  On the other hand, when the liquid refrigerant 92 increases, the degree of supercooling of the refrigerant increases, and the temperature of the refrigerant flowing through the dew condensation prevention pipe 43 decreases. FIG. 14 is a Mollier (pressure-specific enthalpy) diagram when using the third refrigerant circulation passage A of the refrigerator according to the comparative example. As shown in FIG. 13 a, when the third refrigerant circulation passage is used, the refrigerant (section ia) compressed by the compressor 24 is the external radiator 41, the side heat radiation pipe 42, and the dew condensation prevention pipe 43. Since the refrigerant flows in this order, and the refrigerant in the pipe radiates heat to the outside air, the state of the gas phase region (section ab), gas-liquid two-phase region (section bc), and liquid phase region (section cd) Change. The refrigerant flowing out from the dew condensation prevention pipe 43 is decompressed by the capillary tube 45 (section dh) and flows into the cooler 7. Then, the refrigerant that has passed through the cooler 7 and has become low temperature and low pressure absorbs heat from the internal air, the internal air is cooled (section hi), and the refrigerant returns to the compressor 24. Here, when the proportion of the liquid phase region indicated by the section cd increases, the position of d in FIG. 14 is shifted to the left. When the specific enthalpy decreases under the same pressure, the temperature of the refrigerant in the liquid phase region decreases. Therefore, when the position d in FIG. 14 shifts to the left, the temperature of the refrigerant before being depressurized by the capillary tube 45 decreases. That is, the temperature of the refrigerant downstream of the dew condensation prevention pipe 43 decreases.

  In the refrigerator 1 of the comparative example, the partition covers 28a, 29a, 30a are heated by the heat radiation of the dew condensation prevention pipe 43, but when the refrigerant flowing through the dew condensation prevention pipe 43 becomes low temperature, the partition covers 28a, 29a, 30a, The temperature difference with the dew condensation prevention pipe 43 decreases, and the amount of heating per hour by the dew condensation prevention pipe 43 decreases. Therefore, even if only the third refrigerant circulation passage D side is used, condensation occurs at excessively high humidity, and even if condensation can be prevented, the condensation prevention pipe 43 is used to compensate for the decrease in heating amount per hour. It may be necessary to increase the heating time, and the ratio of using the fourth refrigerant circulation flow path E side may be reduced. In addition, in a refrigerator using isobutane, which is a flammable refrigerant, as a comparative example, an upper limit of the refrigerant amount is provided according to IEC (International Electrotechnical Commission) standards and JEMA (Japan Electrical Manufacturers Association) voluntary standards. . Therefore, the refrigerant filling amount cannot be increased excessively, and it is difficult to suppress the refrigerant flow noise in the refrigerator 1 of the comparative example.

  Moreover, in the three-way valve 201 in the refrigerator 1 of the comparative example, the energy saving performance improvement effect obtained in the F state when the compressor 24 is stopped is less than the three-way valve 101 in the refrigerator 1 of the first embodiment. In the three-way valve 101 of the first embodiment, when the compressor 24 is stopped, the three-way valve 101 is set to the C state, and the high temperature refrigerant between the upstream side of the three-way valve 101, that is, between ag in FIG. Energy saving performance is improved. On the other hand, the three-way valve 201 of the refrigerator 1 of the comparative embodiment can only suppress the inflow of refrigerant between af in FIGS. 13a and 13b. That is, in the refrigerator 1 of the comparative example, the inflow of the refrigerant in the dew condensation prevention pipe 43 corresponding to fg in FIG. 13a cannot be suppressed. As can be seen from FIG. 13 a, the ratio of the liquid refrigerant 92 is large in the condensation prevention pipe 43, and the density of the liquid refrigerant 92 is extremely higher than that of the gas refrigerant 91 as described above. There are many refrigerants. Therefore, even if the three-way valve 201 is set to the F state when the compressor 24 is stopped, a large amount of high-temperature refrigerant flows into the cooler 7, so that the energy saving performance improvement effect obtained when the compressor 24 is stopped is small.

(Example 2)
Next, the refrigerant flow path configuration of the refrigerator 1 of Example 2 will be described with reference to FIGS. 15 and 16. In addition, about the member same as Example 1, the same code | symbol is attached | subjected and description is abbreviate | omitted.

  FIG. 15 is a diagram illustrating the arrangement positions of the side heat radiation pipe 42, the dew condensation prevention pipe 43, and the rear heat radiation pipe 47 in the refrigerator according to the second embodiment. FIG. 16 is a diagram illustrating the configuration of the refrigeration cycle (refrigerant flow path) of the refrigerator according to the second embodiment. In the refrigerator 1 of the present embodiment, as shown in FIG. 15, the rear heat radiation pipe 47 indicated by a two-dot chain line in FIG. Between the outer box 1a and the inner box 1b on the side, it is disposed so as to be in contact with the surface of the outer box 1a. As shown in FIG. 16, the refrigerant branching portion 100 and the inlet 101i_B of the three-way valve 101 are connected by the backside heat radiation pipe 47 and the connection pipes 76a and 76b instead of the connection pipe 76 of FIG. Since the dew condensation prevention pipe 43 exchanges heat with the partition covers 28a, 29a, 30a, the freezing temperature zone chamber 60 and the like, the refrigerant also dissipates heat in the dew condensation prevention pipe 43 on the first refrigerant circulation flow path A side. On the other hand, on the second refrigerant circulation passage B side that bypasses the dew condensation prevention pipe 43, heat cannot be radiated by the dew condensation prevention pipe 43, so that the amount of heat radiated from the refrigerant is reduced and the heat cannot be sufficiently radiated. Cycle efficiency may be reduced. Therefore, in the refrigerator 1 of the second embodiment, the back heat radiation pipe 47 is provided in the bypass flow path of the dew condensation prevention pipe 43 as auxiliary heat radiation means, and the heat radiation by the back heat radiation pipe 47 is performed to bypass the condensation prevention pipe 43. Reduces heat loss. Therefore, by using the refrigerator of the present embodiment, the internal heating by the dew condensation prevention pipe 43 is suppressed, and further, the heat radiation amount is compensated by the back surface heat radiation pipe 47, so that the heat radiation amount by bypassing the dew condensation prevention pipe 43 is reduced. Since the decrease can also be suppressed, a refrigerator with higher energy saving performance can be obtained.

  As a method for increasing the heat radiation amount of the second refrigerant circulation channel, a rear heat radiation pipe 47 is provided on the upstream side of the refrigerant channel with respect to the refrigerant branching portion 100, and the same heat radiation is achieved in the second refrigerant circulation channel. It is also conceivable to configure so as to obtain performance. In this case, higher heat dissipation performance can be obtained in the first refrigerant circulation channel than in the embodiment shown in FIG. On the other hand, in the refrigerant flow path constituted by the first refrigerant circulation flow path, the external heat radiator 41, the side heat radiation pipe 42, the rear heat radiation pipe 47, and the dew condensation prevention pipe 43 are configured. Since the refrigerant flow path up to 45 is long, it is conceivable that the refrigerant is insufficient and the refrigeration cycle efficiency is lowered. Therefore, in order to make the heat dissipation amount and the refrigerant flow path length of both flow paths appropriate, first, consider the appropriate flow path length of the first refrigerant circulation flow path and use the second refrigerant circulation flow path. If it is determined that the amount of heat released is insufficient, it is better to add heat radiating means to the second refrigerant circulation passage to supplement the amount of heat released.

  In the present embodiment, the rear heat radiation pipe 47 is provided as auxiliary heat radiation means for supplementing the heat radiation amount of the dew condensation prevention pipe 43, but is not limited to the rear heat radiation pipe 47, for example, a ceiling that radiates heat from the top surface of the refrigerator 1. A surface refrigerant pipe may be provided and disposed instead of the rear heat radiating pipe 47.

(Example 3)
Next, the refrigerant flow path configuration of the refrigerator 1 of Example 3 will be described with reference to FIG. In addition, about the member same as Example 1, the same code | symbol is attached | subjected and description is abbreviate | omitted.

  FIG. 17 is a diagram illustrating the configuration of the refrigeration cycle (refrigerant flow path) of the refrigerator according to the third embodiment. In the refrigerator 1 according to the present embodiment, as the heat exchanging unit 48, the refrigerant in the capillary tube 45, that is, the refrigerant before absorbing heat by the cooler 7 and the refrigerant in the connection pipe 82, that is, after absorbing heat by the cooler 7 are used. There is a place to exchange heat with the refrigerant.

  Generally, a refrigerator using a refrigerant such as isobutane is cooled by including a heat exchanging unit 48 that exchanges heat before and after the cooler 7, that is, between the refrigerant in the capillary tube 45 and the refrigerant in the connection pipe 82. It is known to improve efficiency. Further, when the heat exchanging section 48 is not provided, the connection pipe 82 (see FIG. 4) disposed in the machine room 19 becomes low temperature due to the refrigerant evaporated in the cooler 7, and condensation or frost formation on the connection pipe 82 occurs. Consideration is also required. On the other hand, by providing the heat exchange part 48, the connection pipe 82 can be heated by the high-temperature refrigerant on the heat radiation side, and condensation and frost formation in the machine room 19 can be suppressed. In the refrigerator 1 according to the present embodiment shown in FIG. 17, the heat exchanging portion 48 is provided so as to exchange heat between the entire capillary tube 45 and a part of the connection pipe 82. It is only necessary to provide at least a portion where heat exchange is performed between the refrigerant before absorbing heat and the refrigerant after absorbing heat. For example, heat exchange may be performed between a part of the capillary tube 45 and a part of the connection pipe 81. Good.

  Here, the refrigerant in the gas-liquid two-phase region flows through the three-way valve 201 that switches between the third refrigerant circulation channel D side and the fourth refrigerant circulation channel E side as in the refrigerator of the comparative example shown in FIG. As a means for suppressing an increase in refrigerant flow noise caused by the three-way valve 201 in a refrigerator provided at a location, a means for increasing the above-described refrigerant filling amount can be considered. When the refrigerant filling amount is increased, as described above with reference to the comparative example, the liquid refrigerant is increased and becomes a liquid phase region to the upstream side of the refrigerant flow path, and the ratio of the gas refrigerant 91 of the refrigerant passing through the three-way valve 201 is decreased. However, it is considered that the refrigerant flow noise decreases. On the other hand, as described above with reference to FIG. 14, the liquid phase region increases, the degree of supercooling increases, and problems such as difficulty in preventing condensation at excessively high humidity occur. Further, in the refrigerator equipped with the heat exchanging section 48, when the degree of supercooling increases, the refrigerant temperature when flowing into the capillary tube 45 decreases, the temperature difference between the capillary tube 45 and the connection pipe 82 decreases, and heat exchange occurs. The amount of heat exchange between the refrigerants in the portion 48 decreases. For this reason, the temperature of the connection pipe 82 is unlikely to rise, and condensation or frost formation is likely to occur in the connection pipe 82 in the machine room 19, and the effect of improving the cooling efficiency by the heat exchange unit 48 is also reduced. Therefore, in the refrigerator provided with the heat exchange unit 48, it is not desirable to excessively increase the refrigerant filling amount as compared with the refrigerator not provided with the heat exchange unit 48.

  Therefore, the refrigerator 1 according to the third embodiment includes a three-way valve 101 that switches between the first refrigerant circulation passage A side and the second refrigerant circulation passage B side on the downstream side of the dew condensation prevention pipe 43, so that the refrigerant is sealed. The refrigerant flow noise is suppressed without increasing the amount. Therefore, the refrigerant flow noise caused by the three-way valve 101 is suppressed without reducing the effects of suppressing the dew condensation of the connection pipe 82 by the heat exchange unit 48 and improving the cooling efficiency. That is, it is possible to obtain a refrigerator with high energy saving performance that can sufficiently suppress the internal heating by the dew condensation prevention pipe 43 and the cooling efficiency improvement effect by the heat exchange unit 48 while suppressing the refrigerant flow noise and the condensation of the connection pipe 82. .

  In addition, this invention is not limited to each Example mentioned above, Various modifications are included. For example, each of the above-described embodiments has been described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to one having all the configurations described. Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. . Further, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

  Further, in the present embodiment, the three-way valve 101 is provided on the downstream side of the refrigerant flow path of the dew condensation prevention pipe 43 as a place where the refrigerant in the liquid phase region always flows, but the first refrigerant circulation flow path and the Any refrigerant flow path that is in the liquid phase region on both sides of the second refrigerant circulation flow path B may be used. For example, if a second dew condensation prevention pipe with a small amount of heat release is provided on the downstream side of the three-way valve 101, and if it becomes a liquid refrigerant on the first refrigerant circulation channel A side also on the upstream side of the second dew condensation prevention pipe, Refrigerant flow path switching means may be provided upstream of the second dew condensation prevention pipe. Further, as a heat dissipating means upstream of the refrigerant branching portion 100 that dissipates heat on both the first refrigerant circulation flow path A side and the second refrigerant circulation flow path B side, the external radiator 41 and the side heat radiation pipe However, the present invention is not limited to this. For example, if the refrigerant does not run out, the rear heat radiation pipe 47 of the second embodiment is provided upstream of the refrigerant branching portion 100, and both You may use as a thermal radiation means to thermally radiate in a refrigerant flow path.

1 Refrigerator 2 Cold room (storage room)
3 Ice making room (storage room)
4 Upper freezer room (storage room)
5 Lower freezer compartment (storage room)
6 Vegetable room (storage room)
7 Cooler 8 Cooler storage chamber 9 Fan 10 Heat insulation box 11 Refrigeration chamber duct 13 Refrigeration chamber duct 16 Refrigeration chamber return duct 17 Freezer chamber return port 18 Vegetable chamber return duct 19 Machine room 24 Compressor 28 Upper partition wall ( Partition)
29 Lower partition wall (partition)
30 Refrigerating temperature zone partition wall (partition)
41 External radiator (heat dissipation means)
41a External fan 42 Side heat radiating pipe (heat radiating means)
43 Condensation prevention pipe 44 Dryer 45 Capillary tube (pressure reduction means)
46 Gas-liquid separator 47 Rear heat radiation pipe (auxiliary heat radiation means)
48 Heat exchange section 50 Refrigeration room damper 51 Vegetable room damper 52 Freezing room damper 60 Refrigeration temperature zone room 61 Refrigeration temperature zone room 72-82 Connection piping 100 Refrigerant branch part (branch part)
101 Three-way valve (refrigerant flow path switching means)
102 Two-way valve 110 Door hinge cover 111 Outside air temperature sensor 112 Outside air humidity sensor 200 Refrigerant branch part 201 Three-way valve

Claims (5)

In a refrigerator including a compressor, a decompression unit, a cooler, a plurality of storage chambers, a partition portion that partitions the plurality of storage chambers, and a dew condensation prevention pipe that heats the partition portion,
A heat dissipating means is provided in the refrigerant flow path between the compressor and the dew condensation prevention pipe,
A first refrigerant circulation passage for flowing the refrigerant in the order of the compressor, the heat radiating means, the dew condensation prevention pipe, the pressure reducing means, the cooler, and the compressor;
A second refrigerant circulation passage for flowing the refrigerant in the order of the compressor, the heat dissipation means, the pressure reducing means, the cooler, and the compressor,
The first refrigerant circulation channel and the second refrigerant circulation channel are switched to a location where the refrigerant flowing through the first refrigerant circulation channel and the second refrigerant circulation channel becomes a liquid phase region. A refrigerator provided with a refrigerant flow switching means. In a refrigerator including a compressor, a decompression unit, a cooler, a plurality of storage chambers, a partition portion that partitions the plurality of storage chambers, and a dew condensation prevention pipe that heats the partition portion,
A heat dissipating means is provided in the refrigerant flow path between the compressor and the dew condensation prevention pipe,
A first refrigerant circulation passage for flowing the refrigerant in the order of the compressor, the heat radiating means, the dew condensation prevention pipe, the pressure reducing means, the cooler, and the compressor;
A second refrigerant circulation passage for flowing the refrigerant in the order of the compressor, the heat dissipation means, the pressure reducing means, the cooler, and the compressor,
When the first refrigerant circulation channel is used, the first refrigerant circulation channel and the second refrigerant circulation channel are arranged in the refrigerant channel between the dew condensation prevention pipe and the decompression unit. A refrigerator comprising a refrigerant flow path switching means for switching.   The refrigerator according to claim 1 or 2, wherein the refrigerant channel switching means has a mode in which the first refrigerant circulation channel and the second refrigerant circulation channel are closed. Between the heat radiating means and the refrigerant flow switching means, provided with a branching portion for branching the refrigerant into the dew condensation prevention pipe or the second refrigerant circulation flow path that bypasses the dew condensation prevention pipe,
The refrigerator according to claim 1 or 2, further comprising an auxiliary heat dissipating unit between the branch portion of the second refrigerant circulation channel bypassing the dew condensation prevention pipe and the refrigerant channel switching unit.   3. The refrigerator according to claim 1, wherein heat is exchanged between a connection pipe constituting a refrigerant flow path between the cooler and the compressor and the decompression unit. 4.