JP5879501B2 - refrigerator - Google Patents

Description

  The present invention relates to energy saving of a refrigerator having a freezing room and a refrigeration room, and having the freezing room below the refrigeration room.

  From the viewpoint of ease of use of the freezer compartment, there is a refrigerator in which a freezer compartment is disposed below the refrigerator compartment. On the other hand, there is a refrigerator that enhances the efficiency of the refrigeration cycle by disposing a forced air-cooled condenser at the lower part of the casing to increase the heat dissipation capability.

  Furthermore, from the viewpoint of energy saving, in a refrigerator for home use, a refrigerator that improves the efficiency of the refrigeration cycle by cooling each of the freezer compartment and the refrigerator compartment using one evaporator has been proposed (for example, Patent Document 1). This enhances the efficiency of the refrigeration cycle by cooling the refrigerator compartment having a relatively high air temperature at an evaporation temperature higher than that of the freezer compartment.

  Hereinafter, a conventional refrigerator will be described with reference to the drawings.

  FIG. 6 is a longitudinal sectional view of a conventional refrigerator, FIG. 7 is a configuration diagram of a refrigeration cycle of the conventional refrigerator, and FIG. 8 is a schematic diagram of temperature behavior of the temperature sensor and the upper part of the refrigerator in the conventional refrigerator.

  6 and 7, the refrigerator 11 includes a housing 12, a door 13, legs 14 that support the housing 12, a lower machine room 15 provided in a lower portion of the housing 12, and a refrigerator that is disposed above the housing 12. The chamber 17 has a freezing chamber 18 disposed below the housing 12.

  Further, as components constituting the refrigeration cycle, there are an evaporator 20 housed on the back side of the freezer compartment 18, a compressor 57 and a main condenser 61 housed in the lower machine compartment 15.

  Further, a partition wall 22 that divides the lower machine chamber 15, a fan 23 that is attached to the partition wall 22 to air-cool the main condenser 61, an evaporating dish 58 installed on the upper portion of the compressor 57, a bottom plate 25 of the lower machine chamber 15, and a back plate 26 have.

  In addition, a plurality of intake ports 62 provided in the bottom plate 25 for sucking outside air from the entire lower side of the main condenser 61, discharge ports 63 provided on the back side of the lower machine chamber 15, and on the back side of the housing 12. When there is a spacer 64 and the back surface of the refrigerator 11 is pressed against the wall, the communicating air passage connecting the discharge port 63 of the lower machine room 15 and the upper portion of the housing 12 by grounding the spacer 64 to the back wall. 65 is secured.

  Here, the lower machine chamber 15 is divided into two chambers by a partition wall 22, and a main condenser 61 is housed on the windward side of the fan 23, and a compressor 57 and an evaporating dish 58 are housed on the leeward side.

  Further, as components constituting the refrigeration cycle, a dew-proof pipe 45 and a dew-proof pipe 45 which are located on the downstream side of the main condenser 61 and are thermally coupled to the outer surface of the housing 12 around the opening of the freezer compartment 18. It is located downstream, and has a dryer 46 for drying the circulating refrigerant, and a throttle 47 for connecting the dryer 46 and the evaporator 20 to depressurize the circulating refrigerant.

In addition, an evaporator fan 51 that supplies cold air generated in the evaporator 20 to the refrigerator compartment 17 and the freezer compartment 18, a freezer damper 52 that blocks cold air supplied to the freezer compartment 18, and cold air supplied to the refrigerator compartment 17 It has a refrigerator compartment damper 53 that shuts off, a duct 54 that supplies cold air to the refrigerator compartment 17, an FCC temperature sensor 55 that detects the temperature of the freezer compartment 18, and a PCC temperature sensor 56 that detects the temperature of the refrigerator compartment 17.

  About the conventional refrigerator comprised as mentioned above, the operation | movement is demonstrated below.

  When the temperature detected by the PCC temperature sensor 56 rises to a predetermined ON temperature, the freezer compartment damper 52 is closed while the compressor 57 is stopped, the refrigerator compartment damper 53 is opened, and the evaporator fan 51 is driven. Thereby, the refrigerator compartment 17 is cooled using the evaporator 20 and the low-temperature sensible heat of the frost adhering to the evaporator 20 and the latent heat of fusion of the frost (hereinafter, this operation is referred to as “off-cycle cooling”).

  After a predetermined time from the start of off-cycle cooling, the freezer damper 54 is closed, the refrigerator compartment damper 53 is opened, and the compressor 57, the fan 23, and the evaporator fan 51 are driven. By driving the fan 23, the main condenser 61 side of the lower machine chamber 15 partitioned by the partition wall 22 has a negative pressure, and external air is sucked from the plurality of air inlets 62, and the compressor 57 and the evaporating dish 58 side have a positive pressure. The air in the machine room 15 is discharged to the outside from the plurality of discharge ports 63.

  On the other hand, the refrigerant discharged from the compressor 57 is condensed while leaving a part of the gas while exchanging heat with the outside air in the main condenser 61 and then supplied to the dewproof pipe 45. The refrigerant that has passed through the dew-proof pipe 45 dissipates heat through the housing 12 and condenses while warming the opening of the freezer compartment 18. The liquid refrigerant that has passed through the dew-proof pipe 45 is dehydrated by the dryer 46, depressurized by the throttle 47, and while evaporating by the evaporator 20, it exchanges heat with the air in the refrigerator compartment 17 while cooling the refrigerator compartment 17. Then, it returns to the compressor 57 as a gaseous refrigerant (hereinafter, this operation is referred to as “PC cooling”).

  At this time, since the temperature of the air in the refrigerator compartment 17 is higher than that of the freezer compartment 18 and the temperature of the evaporator 20 is increased by off-cycle cooling, it quickly reaches a high evaporation temperature during PC cooling. be able to.

  Next, when the temperature detected by the PCC temperature sensor 56 falls to a predetermined OFF temperature or the temperature detected by the FCC temperature sensor 55 rises to a predetermined ON temperature, the freezer damper 52 is opened and refrigerated. The chamber damper 53 is closed, and the compressor 57, the fan 23, and the evaporator fan 51 are driven. Thereafter, by operating the refrigeration cycle in the same manner as PC cooling, the freezer compartment 18 is cooled by exchanging heat between the inside air of the freezer compartment 18 and the evaporator 20 (hereinafter, this operation is referred to as “FC cooling”).

  Next, when the temperature detected by the FCC temperature sensor 55 is lowered to a predetermined OFF temperature, the freezer damper 52 and the refrigerator compartment damper 53 are closed, and the compressor 57, the fan 23, and the evaporator fan 51 are stopped (hereinafter referred to as the “freezer compartment damper 52”). This operation is called “cooling stop”). During normal operation, a series of operations of off-cycle cooling, PC cooling, FC cooling, and cooling stop are repeated in order.

  In FIG. 8, section e corresponds to off-cycle cooling, section f corresponds to PC cooling, section g corresponds to FC cooling, and section h corresponds to cooling stop operation. The compressor 57 is driven between the section f and the section g, and is stopped between the section h and the section e. Moreover, the freezer compartment 18 is cooled during the section g, and the refrigerator compartment 17 is cooled between the section e and the section f.

  Here, the reason why the temperature change in the upper part of the refrigerating chamber 17 is large is that the upper part is adjacent to the high temperature outside air, while the lower part is adjacent to the low temperature freezing room 18, so during the non-cooling period. This is because the temperature difference between the upper and lower sides becomes larger and the air volume at the upper part is increased during cooling to quickly cool the upper part at high temperature.

  By this series of operations, the efficiency of the refrigeration cycle can be increased by keeping the temperature of the evaporator 20 at the time of PC cooling higher than that at the time of FC cooling, and the frost adhering to the evaporator 20 is melted by off-cycle cooling. By reusing latent heat, energy can be saved by reducing the capacity of the refrigeration cycle necessary for cooling the refrigerator compartment 17 while reducing heater power (not shown) during defrosting.

Japanese Patent Laid-Open No. 9-236369

  However, in the configuration of the conventional refrigerator, since the compressor 57 having the highest temperature in the refrigeration cycle, the freezer compartment 18 and the evaporator 20 are close to each other, the heat absorption load of the housing 12 is increased. The problem occurs. This is because the wall thickness of the casing 12 that separates the evaporator 20 and the compressor 57 is limited by the height of the evaporator 20 and the compressor 57. On the other hand, when the wall thickness of the casing 12 that separates the evaporator 20 and the compressor 57 is sufficiently secured, for example, the height of the evaporator 20 is restricted, and there is a problem that sufficient heat exchange capability cannot be secured.

  Moreover, in the structure of the said conventional refrigerator, when the back surface of the refrigerator 11 is pressed against a wall, the air temperature in the lower machine room 15 rises, and cooling of the main condenser 61 and the compressor 57 becomes inadequate. As a result, there arises a problem that the durability of the compressor 57 is lowered. This is because when high-temperature air in the lower machine room 15 is discharged from the discharge port 63, a part of the air passes through between the bottom plate 25 and the floor of the refrigerator 11 and is re-inhaled from the intake port 62. The air temperature in the lower machine chamber 15 rises without being sufficiently discharged upward from 65. In addition, since the main condenser 61 and the compressor 57, which are the main heat radiation sources of the refrigeration system, are arranged close to the lower machine chamber 15, it is also compressed that heat radiation is insufficient due to mutual heat effects. This promotes a decrease in durability of the machine 57.

  In the conventional refrigerator configuration, when a part of the air inlet 62 is blocked by dust or dust due to long-term use, the air temperature in the lower machine room 15 rises, and the main condenser 61 and the compressor are compressed. The above-mentioned problem that the cooling of the machine 57 becomes insufficient and, as a result, the durability of the compressor 57 is further deteriorated, and the refrigerating room 17 and the freezing room 18 tend to be slowly cooled due to the performance reduction of the refrigeration system. A problem occurs. This is because the main condenser 61 and the compressor 57, which are the main heat radiation sources of the refrigeration system, are arranged in the lower machine chamber 15, so that the intake port 62 for taking in outside air for cooling the lower machine chamber 15 is blocked. This is because the performance degradation of the refrigeration system due to insufficient heat dissipation occurs remarkably.

  The present invention solves the above-described conventional problems, and appropriately arranges a main condenser and a compressor, which are main heat radiation sources of a refrigeration system, and secures an air passage for cooling, thereby absorbing heat of the casing. It aims at avoiding the problem of the durability fall of the compressor and the performance fall of a refrigerating system which are anxious about long-term use, suppressing load amount.

In order to solve the above-described conventional problems, the refrigerator of the present invention is a refrigerator compartment, a freezer compartment, a casing constituting the refrigerator compartment and the freezer compartment, a refrigeration cycle, and a component of the refrigeration cycle. A compressor, a first auxiliary condenser connecting the compressor and the main condenser, a second auxiliary condenser located downstream of the main condenser, a fan for introducing outside air into the main condenser, A spacer that discharges outside air heat-exchanged with the main condenser to the back side of the casing, and a spacer that is formed on the back side of the casing and secures a communication air passage that communicates the discharge port and the compressor. And the refrigerator is disposed below the refrigerator compartment, the main condenser and the fan are disposed below the refrigerator compartment, and the compressor is disposed above the refrigerator compartment. It intended to, the second auxiliary condenser and the first auxiliary condenser The thermally coupled to the rear of the housing and disposed in contact with the communication air passage, further wherein said first auxiliary condenser is obtained by longer than said second auxiliary condenser.

  By this, when the amount of outside air that cools the main condenser is reduced due to accumulation of dust, dust, etc., by dissipating heat from the natural air-cooled auxiliary condenser facing the communication air passage having an open space above and below, A decrease in the amount of heat released from the refrigeration system can be compensated, and problems such as a decrease in the durability of the compressor and a decrease in the performance of the refrigeration system, which are a concern during long-term use, can be avoided.

  The refrigerator according to the present invention has a main condenser and a compressor that are the main heat radiation sources of the refrigeration system, and has an air passage for cooling, thereby suppressing the heat absorption load of the casing. It is possible to avoid problems such as a decrease in the durability of the compressor and a decrease in the performance of the refrigeration system, which are a concern when used for a period of time.

  In addition, the refrigerator of the present invention can reduce the performance of the refrigeration system, which is a concern when the main condenser is used for a long period of time by increasing the heat dissipation of the main condenser by optimizing the configuration of the lower machine room that houses the main condenser. The problem can be avoided.

The longitudinal cross-sectional view of the refrigerator in Embodiment 1 of this invention Cross-sectional view of the lower machine room refrigerated in Embodiment 1 of the present invention Cycle configuration diagram of refrigerator in Embodiment 1 of the present invention The schematic diagram of the back surface of the refrigerator in Embodiment 1 of this invention Schematic diagram of temperature sensor behavior of refrigerator in embodiment 1 of the present invention Vertical section of a conventional refrigerator Cycle configuration diagram of a conventional refrigerator Schematic diagram of temperature behavior of conventional refrigerator temperature sensor and refrigerated room

The first invention includes a refrigerator compartment, a freezer compartment, a casing constituting the refrigerator compartment and the freezer compartment, a refrigeration cycle, a compressor that is a component of the refrigeration cycle, the compressor, and a main condensation. A first auxiliary condenser connecting the condenser, a second auxiliary condenser located downstream of the main condenser, a fan for introducing outside air into the main condenser, and the outside air heat-exchanged with the main condenser In the refrigerator having the discharge port for discharging to the back side of the housing, and the spacer that is formed on the back side of the housing and that secures a communication air passage that communicates the discharge port and the compressor. The freezer compartment is disposed below the freezer compartment, the main condenser and the fan are disposed below the freezer compartment, and the compressor is disposed above the refrigerator compartment . And the second auxiliary condenser are thermally coupled to the rear surface of the casing and communicated with each other. In contact with the road arranged, further, the first auxiliary condenser by having longer than the second auxiliary condenser, properly positioned the main condenser and the compressor comprising a main radiating source of refrigeration systems, cooling Air flow path for the compressor, reducing the heat absorption load of the housing, and reducing the durability of the compressor and the performance of the refrigeration system
The problem of degradation can be avoided.

According to a second invention, in the first invention, the main condenser, the fan installed on the lee side of the main condenser and serving as a main driving source of the blower circuit, and installed on the lee side of the condenser The evaporating dish is housed in the lower machine room, and air path resistance suppression means is provided on the windward side and leeward side of the fan, thereby reducing the air path resistance around the fan and connecting the main condenser via the intake port. The air volume reduction of the outside air that cools the air can be suppressed, and the heat radiation amount of the main condenser can be increased.

According to a third aspect , in the second aspect , the air path resistance suppression means is provided at a distance greater than the radius of the fan from the fan central portion, thereby further reducing the air path resistance around the fan and via the air inlet. Therefore, it is possible to suppress a reduction in the air volume of the outside air that cools the main condenser, and to increase the heat dissipation amount of the main condenser.

According to a fourth invention, in any one of the first to third inventions, a bottom plate that constitutes a bottom surface of the lower machine chamber, and an intake port that is formed in the bottom plate and sucks outside air from below the main condenser. , And the intake port is arranged on the front side of the bottom plate, so that the outside air sucked from the intake port can flow through the main condenser and heat exchange with the main condenser through the discharge port. When the outside air is discharged to the rear side of the housing, it can be suppressed from taking in again from the air inlet through the gap between the bottom plate and the floor, and the cold air continues to recirculate in the lower machine room And the amount of heat released from the main condenser can be increased.

According to a fifth invention, in any one of the first to fourth inventions, the distance between the back side of the bottom plate and the floor surface is reduced with respect to the distance between the lower side of the main condenser and the floor surface. When the outside air heat-exchanged with the main condenser is discharged to the rear side of the housing through the discharge port, it is possible to further suppress the intake from the intake port through the gap between the bottom plate and the floor surface. It is possible to prevent the cold air from continuing to recirculate in the lower machine room and to increase the heat dissipation of the main condenser.

According to a sixth invention, in any one of the first to fifth inventions, the invention has a back plate that constitutes a back surface of the lower machine room, and the discharge port formed in the back plate. By providing the rising air flow promotion means at the outlet, when the outside air heat-exchanged with the main condenser is discharged to the back side of the housing through the discharge port, the air is sucked again through the gap between the bottom plate and the floor surface. It is possible to further suppress the intake from the mouth, prevent the cold air from continuing to recirculate in the lower machine room, and to increase the heat dissipation of the main condenser.

According to a seventh invention, in any one of the first to sixth inventions, a part of the intake port is blocked by dust adhesion by increasing the area of the intake port relative to the area of the exhaust port. Even in this case, it is possible to suppress a significant decrease in the performance of the condenser due to a decrease in the air volume.

According to an eighth invention, in any one of the first to seventh inventions, comprising: a partition that partitions the main condenser and the evaporating dish; and the fan attached to the partition, wherein the partition and the partition By providing a gap prevention member between the upper surface of the lower machine room and the gap between the partition wall and the upper surface of the lower machine room is sealed, it is possible to suppress a shortcut between the air on the windward side and the leeward side of the fan. At the same time, it is possible to prevent the fan drive sound from propagating to the upper surface of the lower machine room via the partition wall.

According to a ninth invention, in any one of the first to eighth inventions, by arranging a wind direction plate on the upper part of the evaporating dish, the air passing through the main condenser is more reliably near the water surface in the evaporating dish. Evaporation of the stored water can be promoted while increasing the heat radiation amount of the main condenser.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings, but the same reference numerals are given to the same components as those of the conventional example, and detailed description thereof will be omitted. The present invention is not limited to the embodiments.

(Embodiment 1)
1 is a longitudinal sectional view of a refrigerator according to Embodiment 1 of the present invention, FIG. 2 is a transverse sectional view of a lower machine room of the refrigerator according to Embodiment 1 of the present invention, and FIG. 3 is an embodiment of the present invention. FIG. 4 is a schematic diagram of the rear surface of the refrigerator in the first embodiment of the present invention, and FIG. 5 is a schematic diagram of the temperature sensor behavior of the refrigerator in the first embodiment of the present invention.

  1 to 4, the refrigerator 11 includes a housing 12, a door 13, legs 14 that support the housing 12, a lower machine room 15 provided in the lower portion of the housing 12, and an upper portion provided in the upper portion of the housing 12. It has a machine room 16, a refrigeration room 17 disposed at the upper part of the casing 12, and a freezing room 18 disposed at the lower part of the casing 12. In addition, as components constituting the refrigeration cycle, a compressor 19 housed in the upper machine room 16, an evaporator 20 housed in the back side of the freezer room 18, and a main condenser 21 housed in the lower machine room 15 are provided. Have. Further, a partition wall 22 that divides the lower machine chamber 15, a fan 23 that is attached to the partition wall 22 to air-cool the main condenser 21, an evaporating dish 24 installed on the leeward side of the partition wall 22, a bottom plate 25 of the lower machine chamber 15, and a back plate 26 have.

  Here, the main condenser 21 is composed of a spiral fin tube in which strip-shaped fins are wound around the refrigerant pipe, and the refrigerant pipe is spirally wound in an oval shape. And the distance (fin pitch) between refrigerant | coolant piping at the time of spirally winding refrigerant | coolant piping to an oval type is changed so that it may become small toward the leeward side.

  The main condenser 21 is a spiral fin tube, which is advantageous for preventing the air passage from being blocked by dust adhesion, and includes a heat transfer tube in which the refrigerant flows and a fin spirally wound around the outer periphery of the heat transfer tube. Consists of In this embodiment, the heat transfer tube is made of copper and the fin is made of aluminum. However, aluminum or iron may be used for the heat transfer tube, and copper or iron may be used for the fin.

  The refrigerated room 17 is a storage room that is maintained at a low temperature that does not freeze for refrigerated storage, and the specific lower limit of the temperature is usually set to 1 to 5 ° C. In particular, the temperature may be set to 0 to 1 ° C. in order to improve the freshness of fresh products.

  The freezer compartment 18 is a storage room set in a freezing temperature zone. Specifically, it is usually set to −22 to −18 ° C. for frozen storage, but may be set to a low temperature such as −30 ° C. and −25 ° C. for improving the frozen storage state. .

  In addition, when a plurality of air inlets 27 provided in the bottom plate 25, an outlet 28 provided in the back plate 26, a spacer 48 on the back side of the housing 12, and the back of the refrigerator 11 is pressed against the wall By connecting the spacer 48 to the back wall, a communication air passage 29 connecting the discharge port 28 of the lower machine chamber 15 and the upper machine chamber 16 is secured. Here, the lower machine chamber 15 is divided into two chambers by a partition wall 22 and stores a main condenser 21 on the windward side of the fan 23 and an evaporating dish 24 on the leeward side.

  Here, as a wind path resistance suppressing means around the fan, it is preferable to provide an R shape in the front side bent portion 30, the rear side bent portion 31 and the bent portion 32 of the bottom plate 25 in the upper part of the lower machine room 15.

  Moreover, it is preferable to provide the R-shaped part 34 in the evaporating dish 24 with the fan center part 33 as the center. This is because a reduction in the amount of outside air that cools the main condenser 21 via the intake port 27 can be suppressed, and the amount of heat released from the main condenser 21 can be increased.

  Further, the R size of the front side bent portion 30 is preferably about 150 mm, and the R size of the rear side bent portion 31 and the bent portion 32 of the bottom plate 25 is preferably about 50 mm. The R-shaped portion of the bent portion 32 of the front side bent portion 30, the rear-side bent portion 31 and the bottom plate 25 of the lower machine chamber 15 and the R-shaped portion 34 of the evaporating dish 24 are arranged from the fan central portion 33 to the radius of the fan 23. It is desirable to provide the distance above.

  When the distance is within the radius of the fan 23, the air flow resistance around the fan increases, so that the air volume is reduced and the heat dissipation amount of the main condenser 21 is reduced.

  In addition, the air inlet 27 is formed at least 1/2 of the front side of the bottom plate 25, preferably 1/3, and the distance between the back side of the bottom plate 25 where the air inlet 27 is not provided and the floor surface is the main condenser. 21 It is preferable to make it smaller than the distance between the lower side and the floor surface. This is to prevent high-temperature exhaust from the discharge port 28 from being sucked again from the intake port 27 through the space between the bottom plate 25 and the floor surface.

  The clearance between the air inlet 27 and the floor surface should be at least 10 mm or more, preferably 20 mm or more. This is to prevent dust and dust from accumulating between the air inlet 27 and the floor and closing the air inlet 27.

  The bottom plate 25 may be molded by dividing the front side provided with the intake port 27 and the back side provided with no intake port 27. Further, the back side of the bottom plate 25 and the evaporating dish 24 may be integrally formed.

  Further, the position of the discharge port 28 provided in the back plate 26 is preferably provided above the fan central portion 33. This is because when the outside air heat-exchanged with the main condenser 21 is discharged to the back side of the housing 12 through the discharge port 28, the air is again sucked from the intake port 27 through the gap between the bottom plate 25 and the floor surface. This is to suppress this.

  Similarly, it is preferable to provide a wind direction plate 35 for directing exhaust air upward at the exhaust port 28.

  Further, the area of the air inlet 27 provided in the bottom plate 25 may be larger than the area of the outlet 28 provided in the back plate 26. This is for suppressing a significant performance degradation of the main condenser 21 due to a decrease in the air volume even when a part of the air inlet is blocked due to dust adhesion. The area of the intake port 27 is preferably about twice the area of the discharge port 28.

Further, it is preferable to provide a gap preventing member between the partition wall 22 that partitions the lower machine chamber 15 and the back side upper surface 36 of the lower machine chamber 15. This is to prevent the air on the windward side and the leeward side of the fan 23 from being short-circuited by sealing the gap between the partition wall 22 and the back side upper surface 35 of the lower machine room 15. Moreover, it is good to use a buffer material as a clearance prevention member. This is to prevent the driving sound of the fan 23 from propagating to the upper surface 36 on the back side of the lower machine room 15 via the partition wall 22.

  Moreover, it is preferable to arrange a wind direction plate 37 on the top of the evaporating dish 24. This is because the air that has passed through the main condenser 21 meanders downward, and the air is reliably guided to the vicinity of the water surface in the evaporating dish 24, thereby improving the wind speed on the water surface and improving the heat dissipation capability of the main condenser 21. However, it is for promoting evaporation of stored water.

  The size in the width direction of the wind direction plate 37 is equal to or larger than the size in the width direction of the evaporating dish 24 so that the air that has passed through the main condenser 21 can be reliably guided to the vicinity of the water surface in the evaporating dish 24. Is desirable.

  Further, regarding the size of the wind direction plate 37 in the height direction, it is desirable that the lower side of the wind direction plate 37 is about the height of the fan center 31. When the position of the lower side of the wind direction plate 37 is equal to or higher than the height of the fan central portion 33, the air that has passed through the main condenser 21 cannot be reliably guided to the vicinity of the water surface in the evaporating dish 24, and the wind direction plate 37. When the lower side is lower than the height of the fan central portion 33, the airflow direction plate 37 becomes a large airway resistance, and the airflow is reduced, which causes a decrease in the heat radiation amount of the main condenser 21.

  The position of the wind direction plate 37 in the depth direction is more forward than the center of the evaporating dish 24 in the depth direction so that the air that has passed through the main condenser 21 can be reliably guided to the vicinity of the water surface in the evaporating dish 24. It is desirable to arrange.

  In addition, as a component constituting the refrigeration cycle, the compressor 19 and the main condenser 21 are connected, and the auxiliary condenser A49 that is thermally coupled to the back surface of the housing 12 and the downstream side of the main condenser 21 are located in the freezer compartment. A dew-proof pipe 45 that is thermally coupled to the outer surface of the casing 12 around the 18 openings, and is located downstream of the dew-proof pipe 45 and is thermally coupled to the back surface of the casing 12 in a pair with the auxiliary condenser A49. The auxiliary condenser B50 is located on the downstream side of the auxiliary condenser B50, and has a dryer 46 for drying the circulating refrigerant, and a throttle 47 for connecting the dryer 46 and the evaporator 20 to depressurize the circulating refrigerant.

  In addition, it is desirable to make the piping length of the auxiliary condenser A49 longer than the auxiliary condenser B50 and to arrange the inlet piping of the auxiliary condenser A49 at a position separated from the auxiliary condenser B50. This is because the inlet pipe of the auxiliary condenser A49 becomes particularly hot due to the heating steam of the refrigerant discharged from the compressor 19, so that the auxiliary condenser B50 is located on the downstream side of the main condenser 21 and has a relatively low temperature. This is to ensure the heat dissipation capability of the auxiliary condenser B50.

  In addition, the shape of the spacer 48 may be set so that the distance between the casing 12 forming the communication air passage 29 and the rear wall is at least 5 mm or more, preferably 15 mm or more. This is because the air passage resistance of the communication air passage 29 is suppressed when the fan 23 is driven, and the auxiliary condenser A49 and the auxiliary condenser B50 by natural air cooling are used when the intake port 27 is blocked when used for a long time. This is to secure the heat dissipation amount.

In addition, an evaporator fan 38 that supplies cold air generated in the evaporator 20 to the refrigerator compartment 17 and the freezer compartment 18, a freezer damper 39 that blocks the cold air supplied to the freezer compartment 18, and cold air supplied to the refrigerator compartment 17 The refrigerator compartment damper 40 to be shut off, the duct 41 for supplying cold air to the refrigerator compartment 17, the FCC temperature sensor 42 for detecting the temperature of the freezer compartment 18, the PCC temperature sensor 43 for detecting the temperature of the refrigerator compartment 17, the upper part of the refrigerator compartment 17, In particular, a DFP temperature sensor 44 that detects the temperature of the refrigerator compartment 17 above the PCC temperature sensor 43 is provided. Here, the duct 41 is formed along the wall surface where the refrigerator compartment 17 and the upper machine chamber 16 are adjacent to each other, and a part of the cold air passing through the duct 41 is discharged from the vicinity of the center of the refrigerator compartment, and much of the cold air is in the upper machine. After passing through the wall 16 while cooling the adjacent wall surface, it is discharged from the upper part of the refrigerator compartment 17.

  In the present embodiment, the fan 23 is erected substantially perpendicular to the bottom plate 25.

  About the refrigerator in Embodiment 1 of this invention comprised as mentioned above, the operation | movement is demonstrated below.

  When the temperature detected by the DFP temperature sensor 44 rises to a predetermined ON temperature, the freezer damper 39 is closed while the compressor 19 is stopped, the refrigerator damper 40 is opened, and the evaporator fan 38 is driven. Thereby, the refrigerator compartment 17 is cooled using the evaporator 20 and the low-temperature sensible heat of the frost adhering to the evaporator 20 and the latent heat of fusion of the frost (hereinafter, this operation is referred to as “off-cycle cooling”). When the temperature detected by the DFP temperature sensor 44 drops to a predetermined OFF temperature, the freezer damper 39 is closed, the refrigerator compartment damper 40 is closed, and the evaporator fan 38 is stopped (hereinafter, this operation is referred to as “cooling”). Stopped)).

  When the temperature detected by the PCC temperature sensor 43 rises to a predetermined ON temperature during off-cycle cooling or cooling stop, the freezer damper 39 is closed, the refrigerator compartment damper 40 is opened, the compressor 19, the fan 23, and evaporation The fan 38 is driven. By driving the fan 23, the main condenser 21 side of the lower machine chamber 15 partitioned by the partition wall 22 has a negative pressure, and external air is sucked from the plurality of air inlets 27, and the evaporating dish 24 side has a positive pressure. Are discharged to the outside through a plurality of discharge ports 28. The air discharged from the lower machine room 15 is sent to the upper machine room 16 via the communication air passage 29 to cool the compressor 19.

  On the other hand, the refrigerant discharged from the compressor 19 is condensed while leaving a part of the gas while exchanging heat with the outside air in the auxiliary condenser A49 and the main condenser 21, and then supplied to the dew prevention pipe 45 and the auxiliary condenser B50. Is done. The refrigerant that has passed through the dew-proof pipe 45 dissipates heat through the housing 12 and condenses while warming the opening of the freezer compartment 18. The liquid refrigerant that has passed through the auxiliary condenser B50 is water-removed by the dryer 45, depressurized by the throttle 47, and is evaporated by the evaporator 20 while exchanging heat with the air in the refrigerator compartment 17 while cooling the refrigerator compartment 17. Then, it returns to the compressor 19 as a gaseous refrigerant (hereinafter, this operation is referred to as “PC cooling”).

  Here, the auxiliary condenser A49 and the auxiliary condenser B50 warm the back surface of the housing 12, thereby preventing condensation and acting as an auxiliary radiator of the refrigeration system. In addition, by securing the communication air passage 29 with the spacer 48, even when the back surface of the refrigerator 11 is pressed against the wall, the fan 23 is efficiently cooled by the air blown by the fan 23, and the main condenser 21 can be used for a long time. Even when the air flow rate of the fan 23 is reduced due to the blockage, the heat radiation capacity is ensured by natural convection because it faces the communication air passage 29 formed in the vertical direction.

  In addition, it is desirable to arrange | position the inlet side piping of auxiliary condenser A49 into which heated steam with comparatively high temperature flows apart from auxiliary condenser B50 into which much condensed liquid refrigerant flows. Specifically, the piping length of the auxiliary condenser A49 is made longer than that of the auxiliary condenser B50, and the auxiliary condenser A49 is arranged while meandering from one end of the back surface of the housing 12, thereby reducing the temperature of the heating steam. After that, it is desirable to arrange the outlet side pipe of the auxiliary condenser A49 close to the auxiliary condenser B50.

Next, when the temperature detected by the PCC temperature sensor 43 falls to the predetermined OFF temperature or when the temperature detected by the FCC temperature sensor 42 rises to the predetermined ON temperature, the freezer damper 39 is opened and the refrigerator is refrigerated. The chamber damper 40 is closed, and the compressor 19, the fan 23, and the evaporator fan 38 are driven. Thereafter, by operating the refrigeration cycle in the same manner as PC cooling, the freezer compartment 18 is cooled by exchanging heat between the inside air of the freezer compartment 18 and the evaporator 20 (hereinafter, this operation is referred to as “FC cooling”). Next, when the temperature detected by the FCC temperature sensor 42 falls to a predetermined OFF temperature, the cooling stop operation is performed.

  Note that off-cycle cooling operates in preference to cooling stop during cooling stop, and does not operate during PC cooling and FC cooling. In addition, PC cooling and FC cooling are operated with priority over off-cycle cooling. Further, the OFF temperature at which the off-cycle cooling is stopped is set higher than the ON temperature at which the PC cooling is started. As a result, during normal operation, the basic operation is to repeat a series of operations of PC cooling, FC cooling, and cooling stop in order, and while the PC cooling and FC cooling operations are not performed, the cooling stop and off-cycle cooling are performed several times. Repeat repeatedly.

  In FIG. 5, section a corresponds to PC cooling, section b corresponds to FC cooling, section c corresponds to off-cycle cooling, and section d corresponds to cooling stop operation. By this series of operations, the efficiency of the refrigeration cycle can be increased by keeping the temperature of the evaporator 20 at the time of PC cooling higher than that at the time of FC cooling, and the frost adhering to the evaporator 20 is melted by off-cycle cooling. By reusing latent heat, energy can be saved by reducing the capacity of the refrigeration cycle necessary for cooling the refrigerator compartment 17 while reducing heater power (not shown) during defrosting.

  Further, based on the DFP temperature sensor 39 provided in the upper part of the refrigerating chamber 17 having a relatively large temperature change, the off-cooling is performed several times while the PC cooling operation and the FC cooling operation are not performed. Since the ratio between the off-cycle cooling and the PC cooling for cooling 17 can be accurately adjusted, the PC cooling operation time can be appropriately ensured.

  Also, as the detection temperature of the PCC temperature sensor 43 or the FCC temperature sensor 42 increases, even in the case of off-cycle cooling, this is stopped, and PC cooling and FC cooling are switched by preferentially switching to PC cooling or FC cooling. An operation time can be ensured appropriately, and temperature changes in the refrigerator compartment 17 and the freezer compartment 18 can be suppressed.

  Further, by setting the OFF temperature at which the off-cycle cooling is stopped higher than the ON temperature at which the PC cooling is started, the temperature of the DFP temperature sensor 44 provided in the upper part of the refrigerator room 17 having a relatively high temperature is set as the PCC temperature sensor. By controlling the off-cycle cooling while keeping it relatively high, the temperature change in the upper part of the refrigerator compartment 17 can be suppressed. In the first embodiment, the OFF temperature for stopping off-cycle cooling is set higher than the ON temperature for starting PC cooling. However, the OFF temperature for stopping off-cycle cooling is set to OFF for stopping PC cooling. The same effect can be obtained even if the temperature is set higher than the temperature.

  Further, by forming a duct 41 on the wall surface of the refrigerating chamber 17 adjacent to the upper machine chamber 16 that is higher in temperature than the outside air, cool air that cools the refrigerating chamber 17 during off-cycle cooling and PC cooling, particularly the refrigerating chamber 17. By raising the temperature of the cool air that cools the upper part of the refrigerator, it is possible to avoid overcooling of the upper part of the refrigerator compartment 17 and further suppress temperature fluctuations of the upper part of the refrigerator compartment 17, and Since cooling can be avoided, the amount of cool air that cools the refrigerator compartment 17 during PC cooling can be increased, and the efficiency of the heat exchange of the evaporator 20 can be improved to obtain higher refrigeration cycle efficiency during PC cooling. it can.

As described above, the refrigerator of the present invention includes a refrigerator compartment, a freezer compartment, a casing constituting the refrigerator compartment and the freezer compartment, a refrigeration cycle, a compressor that is a component of the refrigeration cycle, A main condenser that mainly cools the refrigerant discharged from the compressor; a fan that introduces outside air into the main condenser; and an outlet that discharges the outside air heat-exchanged with the main condenser to the back side of the housing. In the refrigerator having a spacer formed on the back side of the housing and ensuring a communication air passage communicating the discharge port and the compressor, the freezing chamber is disposed below the refrigerator compartment, The main condenser and the fan are arranged below the freezer compartment, and the compressor is arranged above the refrigerator compartment. As a result, the main condenser and the compressor are arranged apart from each other, while suppressing the mutual thermal influence, it is possible to simultaneously cool using a single fan in the same air path and to compress near the refrigerator compartment. By arranging the machine, it is possible to reduce the heat load of the housing.

  In addition to the above-described configuration, the refrigerator of the present invention includes a natural air cooling type auxiliary condenser that auxiliaryly cools the refrigerant discharged from the compressor together with the main condenser, and connects the auxiliary condenser. It is arranged at a position facing the ventilation path. By this, when the amount of outside air that cools the main condenser is reduced due to accumulation of dust, dust, etc., by dissipating heat from the natural air-cooled auxiliary condenser facing the communication air passage having an open space above and below, A decrease in the amount of heat released from the refrigeration system can be compensated, and problems such as a decrease in the durability of the compressor and a decrease in the performance of the refrigeration system, which are a concern during long-term use, can be avoided.

  Further, the refrigerator of the present invention, the main condenser, the fan installed on the lee side of the main condenser and serving as the main drive source of the blower circuit, the evaporating dish installed on the lee side of the condenser, Is provided in the lower machine room, and air path resistance suppression means is provided on the windward side and leeward side of the fan. As a result, the air path resistance around the fan can be reduced, the reduction of the air volume of the outside air that cools the main condenser via the intake port can be suppressed, and the heat dissipation amount of the main condenser can be increased.

  As described above, the refrigerator according to the present invention appropriately disposes the main condenser and the compressor, which are the main heat radiation sources of the refrigeration system, and secures an air passage for cooling, so that the heat absorption load of the housing It can be applied to other refrigeration and other refrigeration products such as commercial refrigerators because it can avoid the problems of compressor durability and refrigeration system performance that are concerned about long-term use. .

DESCRIPTION OF SYMBOLS 11 Refrigerator 12 Housing | casing 15 Lower machine room 16 Upper machine room 17 Refrigeration room 18 Freezer room 19 Compressor 20 Evaporator 21 Main condenser 23 Fan 28 Outlet 29 Communication air path 48 Spacer 49 Auxiliary condenser A
50 Auxiliary condenser B

Claims (9)

A refrigeration room, a freezing room, a casing constituting the freezing room and the freezing room, a refrigeration cycle, a compressor which is a component of the refrigeration cycle, and a first connecting the compressor and the main condenser. An auxiliary condenser, a second auxiliary condenser located downstream of the main condenser, a fan for introducing outside air into the main condenser, and outside air heat-exchanged with the main condenser on the back side of the casing In the refrigerator having a discharge outlet and a spacer that is formed on the back side of the casing and that establishes a communication air passage that communicates the discharge outlet and the compressor, the freezer compartment below the refrigerator compartment The main condenser and the fan are arranged below the freezer compartment, and the compressor is arranged above the refrigerator compartment , and the first auxiliary condenser and the second auxiliary condenser are arranged. The heat exchanger is thermally coupled to the rear surface of the casing and arranged in contact with the communication air passage. Refrigerator and further, the first auxiliary condenser made longer than the second auxiliary condenser. The main condenser, the fan installed on the lee side of the main condenser and serving as the main drive source of the blower circuit, and the evaporating dish installed on the lee side of the condenser are housed in the lower machine room, The refrigerator according to claim 1 , wherein air path resistance suppression means is provided on the windward side and leeward side of the fan. The refrigerator according to claim 2 , wherein the air path resistance suppression unit is provided at a distance greater than or equal to the radius of the fan from the center of the fan. A bottom plate that constitutes a bottom surface of the lower machine chamber, and an intake port that is formed in the bottom plate and sucks outside air from below the main condenser, and the intake port is disposed on the front side of the bottom plate. The refrigerator as described in any one of 1-3 . The refrigerator according to any one of claims 1 to 4 , wherein the distance between the back side of the bottom plate and the floor surface is made smaller than the distance between the lower side of the main condenser and the floor surface. A rear plate constituting the back of the lower machine chamber, wherein said discharge port formed in the back plate, have any one of claims 1 to 5 in which a rising air promoting means to said exhaust port Refrigerator. The refrigerator according to any one of claims 1 to 6 , wherein an area of the intake port is larger than an area of the discharge port. A partition wall partitioning the evaporation pan to the main condenser, and a said fan which is attached to the partition wall, of claims 1 to 7 in which a gap preventing member between the lower machine chamber upper surface and the partition wall The refrigerator as described in any one. The refrigerator as described in any one of Claim 1 to 8 which arrange | positioned the wind direction board in the upper part of the said evaporating dish.