JP2010060146A - Refrigerator-freezer and cooling storage - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerator-freezer capable of reducing noise with respect to a cooling storage comprising first and second cooling compartments of different temperatures. <P>SOLUTION: This refrigerator-freezer includes: a body section having a heat insulating housing 3 provided with a refrigerating compartment 2 for refrigerating and storing stored objects, and a freezing compartment 4 for freezing and storing stored objects; a first compressor 11 for operating a first refrigerating cycle 10 in which a first refrigerant is circulated; a first evaporator 14 disposed in a low temperature section of the first refrigerating cycle 10 for cooling the refrigerating compartment 2; a second compressor 21 for operating a second refrigerating cycle 20 in which a second refrigerant is circulated; a second evaporator 24 disposed in a low temperature section of the second refrigerating cycle 20 and cooling the freezing compartment 4; a first machine chamber 5 provided with the first compressor 11; and a second machine chamber 6 provided with the second compressor 21. In the refrigerator-freezer, one of the first and second machine chambers 5, 6 is disposed at an upper part of the body section, and the other is disposed at a lower section of the body section. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a refrigerator-freezer provided with first and second compressors for cooling a refrigerator compartment and a freezer compartment, respectively. Moreover, this invention relates to the refrigerator provided with the 1st, 2nd cooling chamber from which temperature differs.

  A conventional refrigerator-freezer is disclosed in Patent Document 1. This refrigerator / freezer has a freezer compartment at the top of the main body and a refrigerator compartment at the bottom. A machine room is provided behind the refrigerator compartment, and the first and second compressors are arranged in the machine room. The first compressor operates the first refrigeration cycle, and the refrigerator compartment is cooled by an evaporator disposed in a low temperature portion of the first refrigeration cycle. The second compressor operates the second refrigeration cycle, and the freezer compartment is cooled by an evaporator disposed in a low temperature part of the second refrigeration cycle. Thereby, a refrigerator compartment and a freezer compartment can be cooled independently, and power saving can be achieved.

Japanese Patent Laid-Open No. 10-153375 (page 3 to page 5, FIG. 1)

  However, according to the conventional refrigerator-freezer, the first and second compressors are arranged in the machine room provided in the lower part of the main body. Since the first and second compressors are point sound sources, the sound emitted from each is superimposed. In addition, when the first and second compressors are close to each other in the same machine room, sounds having the same phase and close frequency are likely to be generated. When the sound of the same phase is superimposed, the sound pressure level is doubled. In addition, a swell sound is likely to be generated by a sound having a close frequency. Therefore, there is a problem that the noise of the refrigerator / freezer increases.

  An object of this invention is to provide the refrigerator-freezer and refrigerator which can reduce a noise.

  In order to achieve the above object, the refrigerator-freezer of the present invention includes a main body having a refrigeration chamber for storing stored items in a refrigerated state and a heat insulating box having a freezing chamber for storing stored items in a frozen state, and a first refrigerant flowing through the first refrigerant. A first compressor that operates one refrigeration cycle, a first evaporator that is disposed in a low temperature portion of the first refrigeration cycle and cools the refrigerator compartment, and a second that operates a second refrigeration cycle through which a second refrigerant flows. A compressor, a second evaporator disposed in a low temperature part of the second refrigeration cycle for cooling the freezing chamber, a first machine chamber in which the first compressor is disposed, and a second compressor in which the second compressor is disposed. And two machine chambers, one of the first and second machine chambers being disposed above the main body portion and the other being disposed below the main body portion.

  According to this configuration, the first and second refrigeration cycles are operated by the first and second compressors, and the first and second refrigerants are circulated to form the low temperature portion and the high temperature portion of the first and second refrigeration cycles, respectively. Is done. The refrigerator compartment is cooled by the first evaporator in the low temperature part of the first refrigeration cycle, and the freezer room is cooled by the second evaporator in the low temperature part of the second refrigeration cycle. The first and second compressors are respectively disposed in first and second machine chambers provided in the main body. For example, the first machine room is provided in the upper part of the main body part, and the second machine room is provided in the lower part of the main body part. Thereby, the first and second compressors are arranged apart from each other.

  Moreover, this invention is a refrigerator-freezer of the said structure, Heat exchange between the 1st heat exchange part distribute | arranged to the back | latter stage of a 1st evaporator, and the 2nd heat exchange part distribute | arranged to the high temperature part of a 2nd refrigerating cycle It is characterized by having an intermediate heat exchanger. According to this configuration, the low-temperature and low-pressure first refrigerant flows into the first heat exchange part of the low-temperature part of the first refrigeration cycle, and the high-temperature and high-pressure second refrigerant flows into the second heat exchange part of the high-temperature part of the second refrigeration cycle. The refrigerant flows in. Thereby, the heat of the second refrigerant is absorbed by the first refrigerant in the intermediate heat exchanger.

  Further, the present invention provides a refrigerator-freezer having the above-described configuration, wherein the refrigeration chamber and the freezer compartment are arranged side by side vertically, and the first and second machine chambers are disposed in the vicinity of the refrigerator compartment and the freezer compartment, respectively. A first evaporator and a second evaporator are disposed behind the refrigerator compartment and the freezer compartment, respectively, and the intermediate heat exchanger is arranged between the first compressor and the second compressor and extends vertically. In addition, the first heat exchange part and the second heat exchange part bend in the vertical direction, and the refrigerant inlet and the refrigerant outlet of the first and second heat exchange parts are provided in the vicinity of the first machine chamber. It is a feature.

  According to this configuration, for example, the refrigerating chamber is disposed above the main body portion, the first machine chamber having the first compressor is disposed at the upper portion of the main body portion, and the freezing chamber is disposed below the main body portion to perform the second compression. A second machine room having a machine is arranged at the lower part of the main body. The first evaporator is disposed on the upper portion of the main body, and the second evaporator is disposed on the lower portion of the main body. The intermediate heat exchanger is provided so as to extend up and down the main body, and is formed by bending in the vertical direction. A refrigerant inlet and a refrigerant outlet are formed at the upper ends of the first and second heat exchange units. The first heat exchange unit has a refrigerant inlet connected to the first evaporator and a refrigerant outlet connected to the first compressor. The second heat exchange unit has a refrigerant inlet disposed on the second compressor side and a refrigerant outlet disposed on the second evaporator side.

  Further, the present invention provides a refrigerator with the above configuration, wherein the first radiator disposed in the high temperature portion of the first refrigeration cycle, the first decompressor disposed downstream of the first radiator, and the second refrigeration cycle A second decompression device disposed downstream of the intermediate heat exchanger; a first heat recovery portion extending vertically to exchange heat between the second refrigerant flowing out of the second evaporator and the first decompression device; And a second heat recovery part extending vertically to exchange heat between the second refrigerant flowing out of the second evaporator and the second decompression device, and the refrigerant inflow side of the first decompression device is connected to the second compressor And the refrigerant inflow side of the second decompression device is provided in the vicinity of the first compressor.

  According to this configuration, the high-temperature and high-pressure first refrigerant flows into the first radiator to dissipate heat, and the first refrigerant is condensed. The first refrigerant condensed by the first radiator flows into the first decompressor, and the first refrigerant is decompressed and expanded to become low-temperature wet steam having a low dryness. The second refrigerant condensed in the intermediate heat exchanger flows into the second decompression device, and the second refrigerant is decompressed and expanded to become low-temperature wet steam having a low dryness.

  The second refrigerant flowing out of the second evaporator absorbs heat by exchanging heat with the first decompression device in the first heat recovery section. Thereby, the enthalpy of a 1st refrigerant | coolant falls and the 1st refrigerant | coolant with higher cooling capability flows into a 1st evaporator. The second refrigerant flowing out of the second evaporator absorbs heat by exchanging heat with the second decompression device in the second heat recovery section. Thereby, the enthalpy of the second refrigerant is lowered, and the second refrigerant having a higher cooling capacity flows into the second evaporator.

  For example, when the first machine room is arranged at the upper part, the second heat recovery part is provided extending vertically, and the refrigerant inflow side of the second decompression device is arranged at the upper part of the main body part. The refrigerant outflow side of the second decompression device is connected to a second evaporator disposed in the lower part. The first heat recovery unit is provided to extend vertically from the upper end of the second heat recovery unit. The refrigerant inflow side of the first decompression device is arranged in the lower part of the main body, and the refrigerant outflow side of the first decompression device is connected to a first evaporator arranged in the upper part.

  According to the present invention, in the refrigerator with the above-described configuration, the first dryer for dehumidifying the first refrigerant before flowing into the first pressure reducing device is disposed in the second machine chamber, and the second refrigerant before flowing into the second pressure reducing device. A second dryer for removing moisture is disposed in the first machine room.

  According to this configuration, the first refrigerant from which moisture has been removed by the first dryer flows into the first decompression device, and the second refrigerant from which moisture has been removed by the second dryer flows into the second decompression device. For example, when the first machine room is arranged at the upper part, the first dryer is arranged at the lower part of the main body part and connected to the refrigerant inflow side of the first decompression device, and the second dryer is arranged at the upper part of the main body part. Connected to the refrigerant inflow side of the decompression device.

  Moreover, the present invention is characterized in that, in the refrigerator-freezer configured as described above, the second dryer is covered with a heat insulating material.

  Further, the present invention is the refrigerator-freezer having the above-described configuration, wherein the intermediate heat exchanger includes a double tube that covers an inner tube with an outer tube, and a first refrigerant flows through the inner tube to form a first heat exchange unit. The second refrigerant flows through the outer pipe in the opposite direction to the first refrigerant to form a second heat exchange part. According to this configuration, the first refrigerant flowing through the inner pipe and the second refrigerant flowing through the outer pipe exchange heat through the inner pipe.

  Further, the present invention is characterized in that the second refrigerator is provided between the second compressor and the intermediate heat exchanger in the refrigerator-freezer configured as described above. According to this configuration, the high-temperature and high-pressure second refrigerant flows into the second radiator and dissipates heat, and the second refrigerant is cooled down. The second refrigerant lowered in temperature by the second radiator is further cooled and condensed by the intermediate heat exchanger.

  Further, the present invention is characterized in that, in the refrigerator-freezer configured as described above, the first and second heat recovery parts are embedded in the back wall of the heat insulation box, and the second radiator is disposed on the back surface of the main body part. It is said.

  Moreover, the present invention is characterized in that, in the refrigerator-freezer configured as described above, the intermediate heat exchanger is embedded in a back wall of the heat insulating box.

  Further, the present invention is characterized in that, in the refrigerator-freezer configured as described above, an accumulator for separating gas and liquid is installed on the refrigerant outflow side of the second evaporator and is not installed on the refrigerant outflow side of the first evaporator. According to this configuration, the second refrigerant flowing out from the second evaporator is gas-liquid separated by the accumulator, and the gas refrigerant is sent to the second compressor. The gas-liquid mixed first refrigerant flowing out from the first evaporator flows into the intermediate heat exchanger, and the first refrigerant becomes a gas refrigerant by heat exchange with the high temperature part of the second refrigeration cycle and is sent to the first compressor. It is done.

  Further, the present invention is characterized in that, in the refrigerator-freezer having the above-described configuration, the heat insulating wall that partitions the refrigerator compartment and the freezing chamber has a heat insulating performance equivalent to that of the peripheral wall of the heat insulating box.

  Moreover, this invention is characterized by using a part of heat radiation of a 1st radiator for the drain water process of a refrigerator-freezer, and prevention of dew condensation in the refrigerator-freezer of the said structure.

  The refrigerator of the present invention is arranged in a main body having first and second cooling chambers, a first compressor that operates a first refrigeration cycle through which a first refrigerant flows, and a low-temperature part of the first refrigeration cycle. The first evaporator that cools the first cooling chamber, the second compressor that operates the second refrigeration cycle through which the second refrigerant flows, and the second cooling chamber that is disposed in the low temperature part of the second refrigeration cycle A second evaporator, a first machine room in which the first compressor is arranged, and a second machine room in which the second compressor is arranged, wherein one of the first and second machine rooms is the main body portion. The other is arranged at the lower part of the main body part.

  According to the present invention, cooling is performed by the first and second evaporators provided in the first and second refrigeration cycles corresponding to the temperatures of the refrigerator compartment and the refrigerator compartment, respectively. Significant reductions can be realized.

  Also, since one of the first and second machine chambers in which the first and second compressors are arranged is arranged at the upper part of the main body and the other is arranged at the lower part, the first and second compressors serving as point sound sources Are placed apart. Since the sound pressure level of the point sound source decreases as the distance increases, the level of noise felt by the user decreases because the sound source is away from the other sound source when approaching one sound source. In addition, since the first and second compressors are arranged in different rooms, it is difficult for sounds having the same phase and the same frequency to be generated. Thereby, while the sound pressure which superimposed the sound of the 1st, 2nd compressor falls, generation | occurrence | production of a wave | undulation can be reduced. Therefore, the noise of the refrigerator / freezer can be reduced.

  Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a side sectional view showing a refrigerator-freezer according to an embodiment. The main body of the refrigerator-freezer 1 has a heat insulating box 3. In the upper part of the heat insulating box 3, a refrigerator compartment 2 for storing stored items in a refrigerator is arranged. The front surface of the refrigerator compartment 2 is opened and closed by a rotating heat insulating door 2a.

  Below the refrigerating room 2, a freezing room 4 for freezing and storing stored items is disposed via a heat insulating wall 7. The freezer compartment 4 is partitioned by a partition wall 8 disposed at the front, and storage cases 4c and 4d are disposed vertically. The front surface of the freezer compartment 4 is opened and closed by drawer-type heat insulating doors 4a and 4b respectively integrated with the storage cases 4c and 4d.

  The heat insulating wall 7 has a heat insulating performance equivalent to that of the peripheral wall (upper wall, bottom wall, side wall, and back wall) of the heat insulating box 3. Thereby, heat exchange between the refrigerator compartment 2 and the freezer compartment 4 is suppressed.

  A first machine room 5 in which a first compressor 11 is arranged is provided at the upper rear of the refrigerator compartment 2. A second machine room 6 in which a second compressor 21 is arranged is provided at the lower rear of the freezer room 4. The first and second compressors 11 and 21 operate first and second refrigeration cycles 10 and 20 (see FIG. 2), the details of which will be described later.

  A first evaporator 14 connected to the first compressor 11 is disposed on the back surface of the refrigerator compartment 2, and a refrigerator refrigerator 15 is disposed above the first evaporator 14. A second evaporator 24 connected to the second compressor 21 is disposed on the back surface of the freezer compartment 4, and a freezer compartment blower 25 is disposed above the second evaporator 24.

  Cold air cooled by exchanging heat with the first evaporator 14 is discharged to the refrigerator compartment 2 by the refrigerator refrigerator 15. The cold air flows through the refrigerator compartment 2 and returns to the first evaporator 14. Thereby, the refrigerator compartment 2 is cooled. The cold air cooled by exchanging heat with the second evaporator 24 is discharged to the freezer compartment 4 by the freezer blower 25. The cold air discharged into the freezer compartment 4 flows through the freezer compartment 4 and returns to the second evaporator 24. Thereby, the freezer compartment 4 is cooled.

  FIG. 2 is a rear perspective view showing piping of the refrigerator 1. FIG. 3 shows a refrigeration cycle of the refrigerator 1. The refrigeration cycle 30 of the refrigerator 1 is a cascade type dual refrigeration cycle in which the first and second refrigeration cycles 10 and 20 are connected by an intermediate heat exchanger 31. In FIG. 2, the first refrigeration cycle 10 is indicated by a solid line, and the second refrigeration cycle 20 is indicated by a broken line.

  The first refrigeration cycle 10 operated by the first compressor 11 includes a first radiator 12, a first dryer 16, a first decompressor 13, and a first evaporator 14 connected by a refrigerant pipe 10a. A first refrigerant such as isobutane flows in the direction of arrow S1 in the refrigerant pipe 10a. That is, the first refrigerant circulates through the first compressor 11, the first radiator 12, the first dryer 16, the first decompressor 13, the first evaporator 14, and the first compressor 11 in this order.

  The first radiator 12 is formed by fixing the refrigerant pipe 10a to a metal plate that covers the back and side surfaces of the main body, and radiates heat to the outside air. Moreover, the 1st heat radiator 12 has the front-surface part 12a and the evaporation part 12b. The front part 12a is embedded in the front part of the partition wall 8 etc. (refer FIG. 1), and prevents the dew condensation in the opening peripheral part of the freezer compartment 4 which contacts the heat insulation doors 4a and 4b by heat radiation. The evaporating unit 12b is disposed in the first machine room 6 and evaporates drain water collected in an evaporating dish (not shown) by heat radiation. Thereby, dew condensation prevention and evaporation of drain water can be performed efficiently by the 1st radiator 12 of the high temperature 1st freezing cycle 10.

  The first dryer 16 is disposed in the second machine chamber 6 and dehumidifies the first refrigerant flowing into the first pressure reducing device 13. The first decompression device 13 is composed of a capillary tube, and forms a first heat recovery section 32 to exchange heat with the second refrigerant flowing out from the second evaporator 24 as will be described later.

  The second refrigeration cycle 20 operated by the second compressor 21 includes a second radiator 22, a second dryer 26, a second decompressor 23, and a second evaporator 24 connected by a refrigerant pipe 20a. A second refrigerant such as isobutane flows in the direction of the arrow S2 in the refrigerant pipe 20a. That is, the second refrigerant circulates through the second compressor 21, the second radiator 22, the second dryer 26, the second decompressor 23, the second evaporator 24, and the second compressor 21 in this order.

  The second radiator 22 is formed by fixing the refrigerant pipe 20a to a metal plate that covers the back surface of the main body, and radiates heat to the outside air. The second dryer 26 is disposed in the first machine room 5. The second decompression device 23 is composed of a capillary tube, and forms a second heat recovery section 33 to exchange heat with the second refrigerant flowing out of the second evaporator 24 as will be described later. An accumulator 28 for separating gas and liquid is provided on the refrigerant outflow side of the second evaporator 24.

  The intermediate heat exchanger 31 includes a first heat exchange part 31 a provided in the first refrigeration cycle 10 and a second heat exchange part 31 b provided in the second refrigeration cycle 20. The first heat exchange unit 31 a is disposed downstream of the first evaporator 14, and the second heat exchange unit 31 b is disposed downstream of the second radiator 22. The first and second heat exchange portions 31a and 31b are formed adjacent to each other and are formed so as to be able to exchange heat via a boundary wall.

  The intermediate heat exchanger 31 is formed of a double pipe having an inner pipe and an outer pipe embedded in the back wall of the heat insulating box 3 (see FIG. 1), and is formed into a U-shaped pipe that extends in the vertical direction and bends at the lower end. Is done. The first refrigerant flows through the inner pipe of the double pipe to form the first heat exchange part 31a, and the second refrigerant flows through the outer pipe to form the second heat exchange part 31b. The first heat exchange part 31a has a refrigerant inlet 31c and a refrigerant outlet 31d formed at the upper end. Similarly, the refrigerant heat inlet 31e and the refrigerant outlet 31f are formed at the upper end of the second heat exchange part 31b, and the first heat exchange part 31a and the refrigerant flow direction are opposite to each other.

  The first and second refrigeration cycles 10 and 20 are provided with first and second heat recovery units 32 and 33, respectively. The 1st, 2nd heat recovery parts 32 and 33 are embed | buried under the back wall of the heat insulation box 3 (refer FIG. 1). The second heat recovery unit 33 is formed so that the second decompression device 23 and the heat exchange unit 33b provided in the second refrigeration cycle 20 are adjacent to each other and can exchange heat via a boundary wall. In the present embodiment, the second heat recovery unit 33 is formed by welding the capillary tube forming the decompression device 23 and the refrigerant tube forming the heat exchange unit 33b.

  The heat exchanging part 33b is arranged downstream of the second evaporator 24, and the low-temperature second refrigerant flowing out from the second evaporator 24 flows therethrough. The refrigerant inflow side of the second decompression device 23 is provided in the upper part of the main body near the first compressor 11. Thereby, the 2nd heat recovery part 33 is extended and formed from the upper part of a main-body part to the lower part where the 2nd evaporator 24 is arranged, and can ensure long heat exchange length.

  The 1st heat recovery part 32 adjoins the 1st decompression device 13 and the heat exchanging part 32b provided in the 2nd freezing cycle 20, and is formed so that heat exchange is possible mutually via a wall surface. In the present embodiment, the first heat recovery unit 32 is formed by welding the capillary tube forming the decompression device 13 and the refrigerant tube forming the heat exchange unit 32b.

  The heat exchanging part 32b is arranged downstream of the heat exchanging part 33b of the second heat recovery part 33, and the low-temperature second refrigerant after flowing out of the second evaporator 24 flows therethrough. The refrigerant inflow side of the first decompression device 13 is provided in the lower part of the main body portion close to the second compressor 21. Thereby, the 1st heat recovery part 32 is extended and formed from the lower part of a main-body part to the upper part by which the 1st evaporator 14 is arranged, and can ensure long heat exchange length.

  In the refrigerator-freezer 1 having the above-described configuration, the first and second refrigerants flow through the refrigerant tubes 10a and 20a by driving the first and second compressors 11 and 21. The first and second compressors 11 and 21 compress the first and second refrigerants to high temperature and high pressure, and the first and second decompression devices 13 and 23 decompress and expand the first and second refrigerants at low temperature and low pressure. To.

  Accordingly, the first and second refrigeration cycles 10 and 20 until the first and second refrigerants flow out of the first and second compressors 11 and 21 and flow into the first and second decompression devices 13 and 23. It becomes the high temperature part. The low temperature of the first and second refrigeration cycles 10 and 20 until the first and second refrigerant flows out of the first and second decompression devices 13 and 23 and flows into the first and second compressors 11 and 21. Part.

  The high-temperature and high-pressure first refrigerant compressed by the first compressor 11 is deprived of heat by the first radiator 12 and condensed. The first refrigerant liquefied by the first radiator 12 is dehumidified by the first dryer 16 to remove moisture. The first refrigerant that has flowed out of the first dryer 16 is decompressed and expanded by the first decompressor 13 and becomes low-temperature wet steam having a low dryness. At this time, the first refrigerant is further lowered in temperature by the first heat recovery unit 32 with heat taken away by the second refrigerant in the low temperature part of the second refrigeration cycle 20.

  The first refrigerant that has become low-temperature wet steam flows into the first evaporator 14, takes heat from the cold air in the refrigerator compartment 2, evaporates, and becomes wet steam with higher dryness. The first refrigerant in the wet vapor state flowing out from the first evaporator 14 flows into the intermediate heat exchanger 31 and evaporates while taking heat from the second refrigerant in the high temperature part of the second refrigeration cycle to become superheated vapor. The first refrigerant that has become superheated steam returns to the first compressor 11. As a result, the first refrigerant circulates and the first refrigeration cycle 10 is operated.

  The high-temperature and high-pressure second refrigerant compressed by the second compressor 21 is deprived of the ambient air by the second radiator 22. The second refrigerant lowered in temperature by the second radiator 22 flows into the intermediate heat exchanger 31 and is deprived of heat by the first refrigerant in the low temperature part of the first refrigeration cycle 10 to be condensed. The second refrigerant liquefied by the second radiator 22 and the intermediate heat exchanger 31 is dehumidified by the second dryer 26 to remove moisture.

  The second refrigerant that has flowed out of the second dryer 26 is decompressed and expanded by the second decompression device 23, and becomes low-temperature wet steam having a low dryness. At this time, the second refrigerant is further lowered in temperature by the second heat recovery unit 32 with heat taken away by the second refrigerant in the low temperature part of the second refrigeration cycle 20. The second refrigerant that has become low-temperature wet steam flows into the second evaporator 24, takes heat from the cold air in the freezer compartment 4 and evaporates to become wet steam.

  The second refrigerant in the wet vapor state that has flowed out of the second evaporator 24 is led to the second heat recovery unit 33 and the first heat recovery unit 32, and takes heat from the high-temperature second refrigerant and the first refrigerant to generate superheated steam. Become. The second refrigerant that has become superheated steam returns to the second compressor 21. As a result, the second refrigerant circulates and the second refrigeration cycle 20 is operated.

  In addition, the rotation speed of the 1st, 2nd compressors 11 and 21 is controlled by an inverter. Thereby, the temperature levels of the first evaporator 14 and the second evaporator 24 are controlled so as to correspond to the temperatures of the refrigerator compartment 2 and the freezer compartment 4, respectively.

  According to the present embodiment, cooling is performed by the first and second evaporators 14 and 24 provided in the first and second refrigeration cycles 10 and 20 corresponding to the temperatures of the refrigerator compartment 2 and the refrigerator compartment 4, respectively. In comparison, the power consumption of the refrigerator-freezer 1 can be significantly reduced.

  In addition, the first machine room 5 in which the first compressor 11 is arranged is arranged at the upper part of the main body part, and the second machine room 6 in which the second compressor 21 is arranged is arranged in the lower part of the main body part. The first and second compressors 11 and 21 serving as point sound sources are arranged apart from each other. The sound pressure level of a point sound source decreases as the distance increases. For example, when the distance is doubled, the sound pressure level is reduced by about 6 dB. For this reason, when approaching one sound source, since it is away from the other sound source, the level of noise felt by the user is reduced.

  In addition, since the first and second compressors 11 and 21 are arranged in different rooms, it is difficult to generate sounds having the same phase and the same frequency. Thereby, while the sound pressure which superimposed the sound of the 1st, 2nd compressors 11 and 21 falls, generation | occurrence | production of a wave | undulation can be reduced. Therefore, the noise of the refrigerator-freezer 1 can be reduced.

  Even if the first machine room 5 is arranged at the lower part of the main body part and the second machine room 6 is arranged at the upper part of the main body part, the noise can be similarly reduced.

  The refrigeration cycle 30 is configured as a cascade type dual refrigeration cycle in which the first and second refrigeration cycles 10 and 20 are connected by an intermediate heat exchanger 31, and the refrigeration chamber 2 is cooled by the first evaporator 14. The freezer compartment 4 is cooled by the second evaporator 24. For this reason, the temperature difference between the first evaporator 14 and the refrigerator compartment 2 can be reduced. Moreover, since the compression ratio of the 1st, 2nd compressors 11 and 21 becomes small, the 1st and 2nd compressors 11 and 21 can be drive | operated with high efficiency. Accordingly, the COP (Coefficient Of Performance) of the refrigeration cycle 30 is improved, and the power consumption of the refrigerator-freezer 1 can be reduced.

  The intermediate heat exchanger 31 may be disposed in parallel with the first evaporator 14. However, when the intermediate heat exchanger 31 is arranged in series in the subsequent stage of the first evaporator 14, the first refrigerant takes heat from the air in the refrigerator compartment 2 by the first evaporator 14 and then flows through the intermediate heat exchanger 31. To do. Therefore, the intermediate heat exchanger 31 performs heat exchange between the sensible heat of the first refrigerant and the sensible heat of the second refrigerant at a portion near the outflow port of the first heat exchanging portion 31a, thereby improving the heat exchange efficiency. it can.

  In addition, the first machine room 5 and the refrigerator compartment 2 are provided in the upper part of the main body, the first evaporator 14 is arranged behind the refrigerator compartment 2, and the second machine room 6 and the freezer compartment 4 are provided in the lower part of the main body part. Two evaporators 24 are arranged behind the freezer compartment 4. The intermediate heat exchanger 31 extends vertically and is bent in the vertical direction at a position away from the first compressor 11, and the refrigerant inlets 31 c and 31 e and the refrigerant outlet are formed in the upper part of the main body near the first machine chamber 5. 31d and 31f are provided.

  Thereby, the connection length of the 1st evaporator 14, the intermediate heat exchanger 31, and the 1st compressor 11 is shortened. Therefore, the piping length of the first refrigeration cycle 10 can be shortened, and the cooling efficiency of the first refrigeration cycle 10 can be further improved.

  In addition, the 1st machine room 5 and the refrigerator compartment 2 may be distribute | arranged to a main-body part lower part, and the 2nd machine room 6 and the freezer compartment 4 may be distribute | arranged to an upper part of a main-body part. At this time, the intermediate heat exchanger 31 may be bent at the upper end, and the refrigerant inlets 31c and 31e and the refrigerant outlets 31d and 31f may be provided at the lower end. That is, the refrigerator compartment 2 and the freezer compartment 4 are arranged side by side vertically, and the first and second machine compartments 5 and 6 are disposed in the vicinity of the refrigerator compartment 2 and the freezer compartment 4, respectively. The intermediate heat exchanger 31 may be bent at a position away from the first compressor 11, and the refrigerant inlets 31 c and 31 e and the refrigerant outlets 31 d and 31 f may be provided in the vicinity of the first machine chamber 5.

  In addition, since the first heat recovery unit 32 that performs heat exchange between the first decompressor 13 and the low-temperature second refrigerant that has flowed out of the second evaporator 24 is provided, the first heat flowing into the first evaporator 14 is provided. The enthalpy of the refrigerant can be reduced. Therefore, the cooling capacity of the first refrigerant flowing into the first evaporator 14 can be further improved.

  Similarly, since the second heat recovery unit 33 that performs heat exchange between the second decompression device 23 and the low-temperature second refrigerant that has flowed out of the second evaporator 24 is provided, the second heat recovery part 33 that flows into the second evaporator 24 is provided. 2 The enthalpy of the refrigerant can be reduced. Therefore, the cooling capacity of the second refrigerant flowing into the second evaporator 24 can be further improved.

  At this time, the refrigerant inflow side of the first decompression device 13 is disposed at the lower part of the main body, and the first heat recovery unit 32 extends upward and is connected to the first evaporator 14. Further, the refrigerant inflow side of the second decompression device 23 is disposed on the upper portion of the main body, and the first heat recovery unit 32 extends downward and is connected to the second evaporator 14. Thereby, the heat exchange length of the 1st, 2nd heat recovery parts 32 and 33 can be lengthened, and the enthalpy of the 1st and 2nd refrigerant | coolant which flows into the 1st, 2nd evaporators 14 and 24 can be reduced reliably. it can.

  In addition, when the 1st compressor 11 and the 1st evaporator 14 are distribute | arranged to the lower part of a main-body part, and the 2nd compressor 21 and the 2nd evaporator 24 are distribute | arranged to an upper part of a main-body part, the 1st decompression device 13 The refrigerant inflow side may be provided in the upper part of the main body, and the refrigerant inflow side of the second decompression device 23 may be provided in the lower part of the main body. That is, the refrigerant inflow side of the first decompression device 13 may be provided in the vicinity of the second compressor 21, and the refrigerant inflow side of the second decompression device 23 may be provided in the vicinity of the first compressor 11.

  Moreover, since the refrigerant | coolant outflow port 31f of the 2nd heat exchange part 31b of the intermediate heat exchanger 31 is provided in a main-body part upper part, the connection of the intermediate heat exchanger 31 and the 2nd pressure reduction apparatus 23 is shortened, and it is 2nd refrigeration cycle. The cooling efficiency of 20 can be further improved. When the 2nd compressor 21 and the 2nd evaporator 24 are arranged at the main-body part upper part, it is good to provide the refrigerant | coolant outflow port 31f of the 2nd heat exchange part 31b in a main-body part lower part. That is, the refrigerant outlet 31f of the second heat exchange part 31b may be provided in the vicinity of the first compressor 11.

  The first machine room 5 and the freezing room 4 may be arranged at the lower part of the main body part, and the second machine room 6 and the refrigerator room 2 may be arranged at the upper part of the main body part.

  In addition, since the first dryer 16 is disposed in the second machine chamber 6 and the second dryer 26 is disposed in the first machine chamber 5, the piping between the first dryer 16 and the first heat recovery unit 32 can be shortened and the second dryer 26 can be shortened. The piping between the two dryers 26 and the intermediate heat exchanger 31 can be shortened.

  In addition, since the second dryer 26 is covered with the heat insulating material 27, it is possible to prevent the temperature rise of the second refrigerant in the low-temperature second refrigeration cycle 20 due to heat intrusion from the first machine chamber 5.

  Further, the intermediate heat exchanger 31 is formed of a double pipe, and the first refrigerant flows through the inner pipe and the second refrigerant flows through the outer pipe. Therefore, the first refrigerant can easily come into contact with the inner pipe serving as a heat exchange surface. Become. Thereby, evaporation of the first refrigerant can be promoted and the first refrigerant can be returned to the first compressor 11. At this time, the second refrigerant comes into contact with the inner tube and the outer tube and condenses due to heat radiation. Moreover, since the flow direction of the 1st, 2nd refrigerant | coolant which distribute | circulates an inner pipe and an outer pipe was made into the reverse direction, the sensible heat by the 1st refrigerant | coolant after evaporation can be efficiently transmitted to the 2nd refrigerant | coolant of an inflow side. Therefore, the cooling efficiency of the refrigeration cycle 30 can be improved.

  Moreover, since the 2nd heat radiator 22 was provided between the 2nd compressor 21 and the intermediate heat exchanger 31, the heat radiation temperature of the 1st, 2nd freezing cycle 10 and 20 whole can be made lower. In addition, the second refrigerant circulates through the second radiator 22 before the heat is taken away by the first refrigerant by the intermediate heat exchanger 31. Thereby, since the 2nd refrigerant | coolant after heat-exchanging with the 2nd heat radiator 22 and thermally radiating is cooled by the intermediate heat exchanger 31, heat exchange can be performed more efficiently.

  Moreover, since the 1st, 2nd heat recovery parts 32 and 33 are embed | buried in the back wall of the heat insulation box 3, and the 2nd heat radiator 22 has been arrange | positioned in the back surface of a main-body part, it concentrates complicated piping on the back surface. Can do. Thereby, a vacuum heat insulating material can be easily arrange | positioned in the heat insulation box 3, and the heat insulation performance of the heat insulation box 3 can be improved.

  Further, since the intermediate heat exchanger 31 is embedded in the back wall of the heat insulating box 3, the relatively low temperature intermediate heat exchanger 31, the second radiator 22, and the first and second heat recovery units 32 and 33 are disposed on the back surface. To be concentrated on. Therefore, the heat loss of the refrigerator-freezer 1 can be reduced.

  Further, the accumulator 28 is installed on the refrigerant outflow side of the second evaporator 24, and no accumulator is installed on the refrigerant outflow side of the first evaporator 14. Since the intermediate heat exchanger 31 is disposed downstream of the first evaporator 14, the first refrigerant can be reliably evaporated. For this reason, even if an accumulator is omitted, it is possible to prevent liquid refrigerant from entering the first compressor 11. Therefore, the cost can be reduced.

  Moreover, since the heat insulation wall 7 which partitions the refrigerator compartment 2 and the freezer compartment 4 was given the heat insulation performance of the same level as the surrounding wall (upper wall, bottom wall, side wall, and back wall) of the heat insulation box 3, from the refrigerator compartment 2 Heat intrusion into the freezer compartment 4 can be reliably prevented. Thereby, the low temperature cool air cooled by the second refrigeration cycle 20 can be used only for cooling the freezer compartment 4. Therefore, the power consumption of the refrigerator-freezer 1 can be further reduced.

  Moreover, since a part of heat radiation of the 1st heat radiator 12 is utilized for prevention of dew condensation by the front surface part 12a, and it is utilized for the drain water process of the refrigerator-freezer 1 by the evaporation part 12b, the 1st heat radiation of the high temperature 1st freezing cycle 10 is carried out. The vessel 12 can efficiently perform dew condensation prevention and drain water treatment.

  In the present embodiment, the same refrigerant such as isobutane is used for the first and second refrigerants, but different refrigerants may be used. At this time, the boiling point of the first refrigerant may be higher than the boiling point of the second refrigerant. Thereby, since the vapor density of the second refrigerant is higher than that of the first refrigerant and the performance of the second refrigeration cycle 20 can be further improved, it is further preferable.

  For example, it can be easily realized by using isobutane (boiling point −12 ° C.) as the first refrigerant and propane (boiling point −40.09 ° C.) or carbon dioxide (boiling point −78.5 ° C.) as the second refrigerant. . All of these refrigerants are natural refrigerants that use substances that exist in large quantities in nature. Therefore, the environmental load of the refrigerator-freezer 1 can be further reduced by increasing the cooling efficiency of the refrigeration cycle using the natural refrigerant.

  In the refrigerator-freezer in which the first and second refrigeration cycles 10 and 20 are independently operated by the first and second compressors 11 and 21 with the intermediate heat exchanger 31 omitted, the first and second machine rooms 5 and 6 are operated. The noise can be reduced by dispersing the components in the upper and lower parts of the main body.

  In addition, the first and second evaporators 14 and 24 are arranged in the first and second cooling chambers having different room temperatures, respectively, and the first and second compressors 11 and 21 are used for the first and second refrigeration cycles 10 and 20. The present invention can be applied to any refrigerator as long as it operates. In other words, the present invention can be applied to refrigeration cycle application equipment centered on a domestic refrigerator-freezer 1.

  According to this invention, it can utilize for the refrigerator refrigerator provided with the 1st, 2nd compressor which cools a refrigerator compartment and a freezer compartment, respectively. Moreover, it can utilize for the refrigerator provided with the 1st, 2nd cooling chamber from which temperature differs.

Side surface sectional drawing which shows the refrigerator-freezer of embodiment of this invention The rear perspective view which shows piping of the refrigerator-freezer of embodiment of this invention The figure which shows the refrigerating cycle of the refrigerator-freezer of embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Refrigerator Refrigerator 2 Refrigeration room 3 Heat insulation box 4 Freezing room 5 1st machine room 6 2nd machine room 7 Heat insulation wall 10 1st freezing cycle 10a, 20a Refrigerant pipe 11 1st compressor 12 1st heat radiator 12a Front part 12b Evaporator 13 First decompressor 14 First evaporator 15 Cold room blower 16 First dryer 20 Second refrigeration cycle 21 Second compressor 22 Second radiator 23 Second decompressor 24 Second evaporator 25 Freezer compartment blower 26 2nd dryer 27 heat insulating material 28 accumulator 30 refrigeration cycle 31 intermediate heat exchanger 32 1st heat recovery part 33 2nd heat recovery part

Claims (14)

  A main body having a refrigerator compartment for storing stored items in a refrigerator and a freezing chamber for storing stored items in a frozen state, a first compressor for operating a first refrigeration cycle through which a first refrigerant flows, and a first A first evaporator that is arranged in a low temperature part of the refrigeration cycle and cools the refrigerator compartment, a second compressor that operates a second refrigeration cycle through which the second refrigerant flows, and a low temperature part of the second refrigeration cycle. A second evaporator that cools the freezer compartment, a first machine chamber in which the first compressor is arranged, and a second machine chamber in which the second compressor is arranged, and the first and second machine chambers One of the above is disposed at the top of the main body, and the other is disposed at the bottom of the main body.   An intermediate heat exchanger is provided that exchanges heat between a first heat exchanging part disposed downstream of the first evaporator and a second heat exchanging part disposed in a high temperature part of the second refrigeration cycle. The refrigerator-freezer according to claim 1.   The refrigerator compartment and the freezer compartment are arranged in parallel up and down, and the first and second machine compartments are arranged in the vicinity of the refrigerator compartment and the freezer compartment, respectively, and the first behind the refrigerator compartment and the freezer compartment, respectively. An evaporator and a second evaporator are disposed, and the intermediate heat exchanger is disposed between the first compressor and the second compressor and extends vertically, and the first heat exchange unit and the second heat exchanger are disposed. 3. The refrigerator-freezer according to claim 2, wherein the heat exchange part is bent in the vertical direction, and the refrigerant inlet and the refrigerant outlet of the first and second heat exchange parts are provided in the vicinity of the first machine room.   A first radiator disposed in a high-temperature part of the first refrigeration cycle; a first decompressor disposed in a stage subsequent to the first radiator; and a first radiator disposed in a stage subsequent to the intermediate heat exchanger in the second refrigeration cycle. A first heat recovery part extending vertically to exchange heat between the second decompressor, the second refrigerant flowing out from the second evaporator and the first decompressor, and a second refrigerant flowing out from the second evaporator A second heat recovery section extending vertically to exchange heat with the second decompression device, and the refrigerant inflow side of the first decompression device is provided in the vicinity of the second compressor, and the refrigerant of the second decompression device The refrigerator-freezer according to claim 3, wherein the inflow side is provided in the vicinity of the first compressor.   A first dryer for dehumidifying the first refrigerant before flowing into the first decompression device is disposed in the second machine chamber, and a second dryer for dehumidifying the second refrigerant before flowing into the second decompression device is provided in the first machine chamber. The refrigerator-freezer according to claim 4, wherein the refrigerator-freezer is disposed in the refrigerator.   6. The refrigerator-freezer according to claim 5, wherein the second dryer is covered with a heat insulating material.   The intermediate heat exchanger comprises a double pipe that covers an inner pipe with an outer pipe, a first refrigerant flows through the inner pipe to form a first heat exchange part, and a second refrigerant is a first refrigerant. The refrigerator-freezer according to any one of claims 4 to 6, wherein the second heat exchange part is formed by flowing in a direction opposite to that of the refrigerator.   The refrigerator-freezer according to any one of claims 4 to 7, wherein a second radiator is provided between the second compressor and the intermediate heat exchanger.   9. The refrigerator-freezer according to claim 8, wherein the first and second heat recovery units are embedded in the back wall of the heat insulating box, and the second radiator is disposed on the back surface of the main body unit.   The refrigerator-freezer according to claim 9, wherein the intermediate heat exchanger is embedded in a back wall of the heat insulating box.   The accumulator which isolate | separates gas-liquid is installed in the refrigerant | coolant outflow side of a 2nd evaporator, and is not installed in the refrigerant | coolant outflow side of a 1st evaporator, The one in any one of Claims 2-10 characterized by the above-mentioned. Freezer refrigerator.   The refrigerator-freezer according to any one of claims 1 to 11, wherein a heat insulating wall that partitions the refrigerator compartment and the freezing chamber has a heat insulating performance equivalent to a peripheral wall of the heat insulating box.   13. The refrigerator-freezer according to claim 1, wherein a part of heat radiation of the first radiator is used for drain water treatment and prevention of dew condensation of the refrigerator-freezer.   A main body having first and second cooling chambers, a first compressor that operates a first refrigeration cycle through which a first refrigerant flows, and a low temperature portion of the first refrigeration cycle are provided to cool the first cooling chamber. A first evaporator, a second compressor that operates a second refrigeration cycle through which a second refrigerant flows, a second evaporator that is disposed in a low temperature part of the second refrigeration cycle and cools the second cooling chamber, A first machine room in which one compressor is arranged, and a second machine room in which a second compressor is arranged, and one of the first and second machine rooms is arranged at the upper part of the main body, and the other Is disposed in the lower part of the main body.

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