JP2007271138A - Refrigerating machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact and efficient hybrid type magnetic refrigeration device. <P>SOLUTION: In the hybrid refrigerating machine, an evaporator of a vapor compression refrigerating cycle and a heat exchanger of a magnetic refrigerating cycle are thermally connected. The magnetic refrigerating cycle is provided with a magnetic refrigeration unit, and in the magnetic refrigeration unit, a magnetic body generates or absorbs heat in response to increase or reduction of a magnetic field to heat or cool a coolant circulating in its neighborhood. The heated coolant is cooled by the evaporator of the vapor compression refrigerating cycle, and the cooled coolant is supplied to the heat exchanger cooling an ambient atmosphere of an exterior. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

    The present invention relates to a refrigerator, and more particularly, to a refrigerator used for home use, consumer use, and business use.

    Conventionally, a vapor compression refrigeration cycle is generally used as a refrigerator for household, consumer use, and business use (refrigeration capacity: about 0.1 to 1 kW). As is well known, this vapor compression refrigeration cycle includes a compressor for compressing a refrigerant and an expansion valve for expanding the refrigerant, and a condenser for releasing heat from the refrigerant to a refrigerant flow path between the compressor and the expansion valve. In addition, an evaporator for absorbing heat into the refrigerant is disposed. Therefore, in this vapor compression refrigeration cycle, the refrigerant supplied from the compressor releases heat by the condenser, and the refrigerant supplied from the condenser is expanded by the expansion valve and supplied to the evaporator, and the refrigerant absorbs heat. Then, the refrigerant is again supplied to the compressor and compressed. The characteristics of this vapor compression refrigeration cycle are given as a temperature-entropy diagram (Ts diagram) and a pressure-enthalpy diagram (ph diagram), and the reversible cycle is explained by both diagrams.

Further, in a special application limited to a cryogenic environment, Patent Document 1 discloses a magnetic refrigeration cycle that uses a magnetic material (so-called magnetic working substance) that generates and absorbs heat by increasing or decreasing a magnetic field. In this magnetic refrigeration cycle, a superconducting magnet that applies a magnetic field is disposed in a refrigerant flow path between heat exchangers, and a magnetic working material having a magnetocaloric effect is taken in and out of the magnetic field. Therefore, in this magnetic refrigeration cycle, heat generation and heat absorption from the magnetic working material are given to the refrigerant in the refrigerant flow path along with the magnetizing action and demagnetizing action on the magnetic working material, and the cooled refrigerant is supplied to the cooler. The supplied and heated refrigerant is supplied to the exhaust heat exchanger. Magnetic working substances are not limited to materials that generate heat by applying a magnetic field and absorb heat by demagnetizing the magnetic field, but materials that absorb heat by applying a magnetic field and generate heat by demagnetizing the magnetic field are known.
JP 2002-106999 A

  In recent years, there is an increasing demand for refrigerators that can be cooled to low temperatures (-30 ° C or lower) in household, consumer and business applications such as food freshness confinement using quick freezing (-30 ° C or lower). . However, in the conventional vapor compression refrigeration cycle generally used in homes and the like, it is required to increase the compression ratio in order to realize a low temperature range (−30 ° C.). If such a request is met, there is a risk that the lubricating oil or coefficient of performance (COP) in the refrigerator will be deteriorated. As a countermeasure, a multi-stage compression single-stage expansion refrigeration cycle is generally adopted. However, it is complicated as a refrigeration system, incurs high cost of the apparatus, and is not suitable for home and consumer use. Yes.

  In contrast to such a multi-stage compression single-stage expansion refrigeration cycle, the magnetic refrigeration cycle is very useful for causing a large temperature difference in a magnetic refrigeration cycle using a magnetic material having a magnetocaloric effect known so far. A large magnetic field increase / decrease is required. Therefore, a considerably large and complicated device such as a superconducting magnet is required. A magnetic material capable of generating a large temperature difference even in a low magnetic field that can be realized with a permanent magnet has already been developed, and a magnetic refrigeration cycle using such a magnetic material has already been disclosed in Patent Document 1.

  The present invention has been made in view of the above-described circumstances, and is to provide a compact and highly efficient refrigerator.

According to this invention,
A compressor for compressing the first refrigerant;
An expansion valve for expanding the first refrigerant;
A condenser for dissipating the heat of the first refrigerant, provided in a flow path of the first refrigerant flowing from the compressor to the expansion valve;
An evaporator provided in the flow path of the first refrigerant flowing from the expansion valve to the compressor, for absorbing heat from the outside by the first refrigerant;
A pump for circulating the second refrigerant;
A magnetic body that generates heat and absorbs heat in accordance with an increase and decrease in the magnetic field;
A magnet for increasing and decreasing the magnetic field on the magnetic body;
A first heat exchanger that is thermally coupled to the evaporator and that cools the second refrigerant by being supplied with the second refrigerant;
An endothermic part that cools the second refrigerant using a magnetic material that absorbs heat due to the increase and decrease of the magnetic field;
A second heat exchanger that cools an object to be cooled by being supplied with the second refrigerant cooled by the heat absorption unit;
A refrigerator is provided.

Moreover, according to this invention,
A compressor for compressing the first refrigerant;
An expansion valve for expanding the first refrigerant;
A condenser for dissipating the heat of the first refrigerant, provided in a flow path of the first refrigerant flowing from the compressor to the expansion valve;
An evaporator provided in the flow path of the first refrigerant flowing from the expansion valve to the compressor, for absorbing heat from the outside by the first refrigerant;
A pump for circulating the second refrigerant;
A branching portion for branching the second refrigerant from the pump into a first refrigerant flow path provided with the evaporator and a second refrigerant flow path provided with the condenser;
A merge portion that merges the first and second refrigerant flow paths and returns them to the pump;
A magnetic body that generates heat and absorbs heat in accordance with an increase and decrease in the magnetic field;
A magnet for increasing and decreasing the magnetic field on the magnetic body;
A heat-absorbing part that is provided in the first refrigerant flow path and cools the second refrigerant using a magnetic material that absorbs heat due to the increase and decrease of the magnetic field;
A heat generating part that is provided in the second refrigerant flow path and heats the second refrigerant using a magnetic material that generates heat due to the increase and decrease of the magnetic field;
A refrigerator is provided.

  According to this invention, it is possible to provide a compact and highly efficient refrigerator that can be cooled to a low temperature range that can be used for household, consumer and business purposes.

  Hereinafter, a refrigerator, for example, a hybrid magnetic refrigeration apparatus according to an embodiment of the present invention will be described with reference to the drawings as necessary.

  FIG. 1 schematically shows a hybrid magnetic refrigeration apparatus according to a first embodiment of the present invention. The hybrid magnetic refrigeration apparatus shown in FIG. 1 has a vapor compression refrigeration cycle 1 and a magnetic refrigeration cycle 10. That is, the hybrid type magnetic refrigeration apparatus shown in FIG. 1 includes a heat exchange connecting portion 8 that thermally connects the vapor compression refrigeration cycle 1 and the magnetic refrigeration cycle 10. 1 evaporator 2 and the high temperature side heat exchanger 11 of the magnetic refrigeration cycle 10 are thermally coupled for heat exchange.

  As shown in FIG. 1, the vapor compression refrigeration cycle 1 is provided with a compressor 3 for compressing a refrigerant and an expansion valve 5 for expanding the refrigerant, and a condenser 4 is provided in the refrigerant flow path between the compressor 3 and the expansion valve 5. And the evaporator 2 in the heat exchange connection part 8 is connected. Therefore, the refrigerant in the refrigeration cycle 1 is pressurized by the compressor 3, the pressurized refrigerant is supplied to the condenser 4, and the heat of the pressurized refrigerant is dissipated by the condenser 4. The pressurized refrigerant is supplied from the condenser 4 to the expansion valve 5, expanded by the expansion valve 5, and supplied to the evaporator 2. In the evaporator 2, the expanded refrigerant absorbs heat and takes heat from the high temperature side heat exchanger 11 of the magnetic refrigeration cycle 10 that is thermally connected to the evaporator 2 of the vapor compression refrigeration cycle 1. Here, the evaporator 2 of the vapor compression refrigeration cycle 1 cools the heat exchanger 11 of the magnetic refrigeration cycle 10 to approximately 0 ° C. or less, preferably in the range of 0 ° C. to −10 ° C.

  The magnetic refrigeration cycle 10 includes a pump 14 that supplies a refrigerant into the heat exchange connection unit 8. The refrigerant cooled by the heat exchange connection unit 8 is supplied to the heat exchanger 16, and the object to be cooled, for example, the inside of a freezer ( The refrigerant exchanged with the heat exchanger 16 is circulated so as to be supplied to the pump 14 again. The heat exchange connecting portion 8 includes a magnetic refrigeration unit 12 having a heat exchanger 11, a heat generating portion 12A and a heat absorbing portion 12B, and the heat exchanger 11 and the heat generating portion of the magnetic refrigeration unit 12 on the high temperature portion side of the magnetic refrigeration cycle 10. 12A is arranged, and the heat exchanger 16 and the heat absorption part 12B of the magnetic refrigeration unit 12 are arranged on the low temperature part side of the magnetic refrigeration cycle 10. The magnetic refrigeration unit 12 includes a magnet device 18 that applies a magnetic field to the heat generating part 12A, and an external actuator 22 is provided so that the magnetic body 20 having a magnetocaloric effect can move between the heat generating part 12A and the heat absorbing part 12B. It is connected. This magnetic body has a characteristic (magnetocaloric effect) that generates heat and absorbs heat in accordance with increase and decrease of the magnetic field. The magnetic body 20 that moves between the heat generating portion 12A and the heat absorbing portion 12B is disposed in a cylindrical housing as will be described later, and is moved in a piston manner. When a magnetic field is applied to the magnetic body 20, the magnetic body 20 generates heat (heat dissipation), and the magnetic body 20 has a positive magnetic effect in which the magnetic body 20 absorbs heat (cools) by demagnetization of the magnetic body 20. When incorporated in the refrigeration unit 12, the magnet device 18 is disposed on the high temperature part side of the magnetic refrigeration cycle 10 as shown in FIG. 1. When the magnetic body 20 has a negative magnetic effect, the magnet device 18 is disposed on the low temperature part side of the magnetic refrigeration cycle 10. Here, in the magnetic body 20 having a negative magnetic effect, when a magnetic field is applied to the magnetic body 20, the magnetic body 20 absorbs heat (cools), and demagnetization of the magnetic body 20 causes the magnetic body 20 to generate heat (heat dissipation). )

  In this magnetic refrigeration cycle 10, the magnetic refrigeration unit 12 is disposed on the high temperature part side and the low temperature part side of the magnetic refrigeration cycle 10, but the high temperature part side of the magnetic refrigeration unit 12 so that heat is not transmitted between them. And between the low temperature part side, ie, between the heat generating part 12A and the heat absorption part 12B, the heat insulation structure 24 is provided.

  In the magnetic refrigeration cycle 10 shown in FIG. 1, the refrigerant supplied from the pump 14 is cooled to the temperature of the evaporator 2 by a heat exchanger 11 thermally connected to the evaporator 2 of the vapor compression refrigeration cycle 1. And supplied to the heat generating part 12A of the magnetic refrigeration unit 12. In the heat generating portion 12A of the magnetic refrigeration unit 12, the refrigerant is heated (temperature rises) by the heat generated by the magnetic body 20, but is cooled in advance by the heat exchanger 11 and provided adjacent to the heat exchanger 11. And being provided with the heat insulating structure 24, it is maintained at a relatively low temperature, for example, around 0 ° C. The refrigerant maintained at a relatively low temperature is similarly supplied to the heat absorption unit 12B of the magnetic refrigeration unit 12 with the pressure of the pump 14. In the heat absorption part 12B, the refrigerant is deprived of heat by the magnetic body 20, and is further cooled to, for example, -20 ° C to -30 ° C. The sufficiently cooled refrigerant is supplied to the heat exchanger 16 on the low temperature part side of the magnetic refrigeration cycle 10 and is returned to the pump 14 again through the heat exchanger 16. In the heat exchanger 16 on the low temperature part side of the magnetic refrigeration cycle 10, the external environment is cooled by the supplied refrigerant.

  The cooling temperature difference in each of the vapor compression refrigeration cycle 1 and the magnetic refrigeration cycle 10 shown in FIG. 1 is in the range of about 20 ° to 30 ° C., and preferably 30 ° C. or more. Therefore, if the vapor compression refrigeration cycle 1 can cool to about 0 ° C., the ambient temperature can be cooled to −30 ° C. or less by the heat exchanger 16 of the magnetic refrigeration cycle 10.

  FIG. 2 shows an example of the structure of the magnetic refrigeration unit 12 shown in FIG. As shown in FIG. 1, the pipe 42 through which the vapor refrigeration refrigerant flows and the pipe 44 through which the magnetic refrigeration refrigerant circulate intersect at a connecting portion 8, and the evaporator 2 and the magnetic refrigeration of the vapor refrigeration cold cycle shown in FIG. 1. The high temperature side heat exchanger 11 of the cycle 10 is thermally connected. That is, in the connecting portion 8, the pipes 42 and 44 are arranged in a nested structure. The magnetic refrigeration refrigerant pipe 44 is U-shaped, and one of the U-shaped magnetic refrigeration refrigerant pipes 44 corresponds to the high temperature portion side pipe portion 44A of the magnetic refrigeration cycle 10, and the U-shaped magnetic refrigeration refrigerant pipe 44 The other of 44 corresponds to the low temperature part side pipe part 44 </ b> B of the magnetic refrigeration cycle 10. A cylindrical portion 48 is pierced through the high temperature portion side pipe portion 44A and the low temperature portion side pipe portion 44B and slidably accommodates the magnetic body 20, and the pipe portions 44A, 44B and the cylindrical portion 48 have a nested structure. It is composed. Outside the cylindrical part 48, an actuator 22 for selectively moving the magnetic body 20 to the high temperature part side pipe part 44A and the low temperature part side pipe part 44B is provided. In addition, permanent magnets 50 are arranged on both sides of the high temperature part side pipe part 44 </ b> A from which the cylindrical part 48 extends, and a magnetic field can be applied to the magnetic body 20 in the cylindrical part 48 by the permanent magnet 50. . Therefore, the high temperature part side and the low temperature part side of the cylindrical part 48 to which the magnetic field is applied from the permanent magnet 50 are determined as the heat generating part 12A and the heat absorbing part 12B of the magnetic refrigeration unit 12. In addition, although the heat insulation structure 24 is provided between the high temperature part side pipe part 44A and the low temperature part side pipe part 44B, illustration of the heat insulation structure 24 is abbreviate | omitted for convenience of the description in FIG.

  In the structure of the magnetic refrigeration unit 12 shown in FIG. 2, the vapor refrigeration refrigerant is circulated through the pipe 42, the magnetic refrigeration refrigerant is circulated through the pipe 44, and the magnetic refrigeration refrigerant is cooled by the vapor refrigeration refrigerant at the connecting portion 8. . The cooled refrigerant flows from the high temperature part side pipe part 44A to the low temperature part side pipe part 44B. In the high temperature part side pipe part 44A, when the magnetic body 20 is moved to the heat generating part 12A on the high temperature part side of the cylindrical part 48, the magnetic body 20 is heated by the application of a magnetic field, and between the magnetic refrigeration refrigerant. Heat exchanged. The temperature of the magnetic refrigeration refrigerant rises as the magnetic body 20 radiates heat, but the magnetic refrigeration refrigerant is cooled in advance, provided adjacent to the heat exchanger 11, and further provided with a heat insulating structure 24. Therefore, the magnetic refrigeration refrigerant is circulated to the low temperature portion side pipe portion 44B while being maintained at a relatively low temperature. When the magnetic body 20 is moved to the endothermic part 12B on the low temperature part side of the cylindrical part 48, the magnetic body 20 gives an endothermic action to the magnetic refrigeration refrigerant, and the cooled magnetic refrigeration refrigerant becomes the low temperature part side pipe part. It is supplied to the heat exchanger 16 through 44B.

  In the structure shown in FIG. 2, one connecting portion 8 is illustrated, a pair of permanent magnets 50 is disposed at two locations, and a cylindrical portion 48 is disposed between the two permanent magnets 50. A plurality of connecting portions 8 are provided, and a combination of the permanent magnet 50 and the cylindrical portion 48 is disposed at one location or a plurality of locations of three or more locations, and the low temperature portion side pipe portion 44B has one or more of a plurality of heat absorptions. It is obvious that the magnetic refrigeration refrigerant may be cooled to a lower temperature by providing the portion 12B. Further, in the arrangement shown in FIG. 2, it is obvious that an electromagnet may be provided instead of the permanent magnet 50 as apparent. Further, as shown in FIG. 2, it is preferable to provide a heat generating portion 12 </ b> A upstream of the connecting portion 8 with respect to the direction in which the magnetic refrigeration refrigerant flows. This is because the temperature difference between the magnetic refrigeration refrigerant and the refrigerant of the vapor compression refrigeration cycle 1 at the connecting portion 8 can be made large, so that the amount of heat transferred between the magnetic refrigeration refrigerant and the refrigerant of the vapor compression refrigeration cycle 1 is increased. This is because the COP can be increased.

  In addition, when the magnetic body 20 has a negative magnetic effect instead of a positive magnetic effect, it is clear that the permanent magnet 50 or the electromagnet is provided in the low temperature part side pipe part 44B. There is no restriction on the time cycle in which the magnetic body 20 is magnetized and demagnetized, and it may be determined appropriately according to the cooling characteristics realized by the magnetic refrigeration cycle 10. In addition, the independent actuator 22 is not provided, and the magnetic body 20 may be moved by using the mechanical operation or other mechanical operation of the piston or cylinder of the compressor 3 used in the vapor compression refrigeration cycle.

  In the hybrid magnetic refrigeration apparatus shown in FIGS. 1 and 2, the refrigerant in the magnetic refrigeration cycle is cooled by the vapor compression refrigeration cycle and further cooled by the magnetic refrigeration cycle. Can be realized. Since the refrigerant circulating in the magnetic refrigeration cycle is cooled in advance as compared with the case where the same cooling is realized only by the magnetic refrigeration cycle, the magnetic refrigeration apparatus can be made compact.

  FIG. 3 schematically shows a refrigerator, for example, a hybrid magnetic refrigeration apparatus, according to another embodiment of the present invention. In FIG. 3, the same parts or devices as those shown in FIG.

  A vapor compression refrigeration cycle 1 in the hybrid magnetic refrigeration apparatus shown in FIG. 3 is provided with a liquid receiver 6 that stores liquefied refrigerant between a condenser 4 and an expansion valve 5. That is, the refrigerant is compressed and liquefied by the compressor 3, heat is released from the liquefied refrigerant by the condenser 4, and the liquefied refrigerant is temporarily stored in the liquid receiver 6. The liquefied refrigerant is supplied from the liquid receiver 6 to the expansion valve 5 and is expanded and vaporized, and the vaporized refrigerant is supplied to the evaporator 2 so that the evaporator 2 takes heat from the periphery.

  In the hybrid magnetic refrigeration apparatus shown in FIG. 3, the connection unit 8 is provided with an evaporator 2 of the vapor compression refrigeration cycle 1 and a heat exchanger 11 of the magnetic refrigeration cycle, and the evaporator 2 of the vapor compression refrigeration cycle 1. As a result, the heat exchanger 11 of the magnetic refrigeration cycle is cooled. Moreover, the heat exchanger 11 of this magnetic refrigeration cycle is provided on the high temperature side of the magnetic refrigeration cycle.

  In the magnetic refrigeration cycle 30 shown in FIG. 3, the refrigerant from the pump 32 is branched into two refrigerant flow paths on the low temperature side and the high temperature side at the branching portion, merged again at the junction, and returned to the pump 32. . The refrigerant flow path on the low temperature side is provided with a heat absorption part 12B of the magnetic refrigeration unit 12, and the refrigerant passes through the heat absorption part 12B and is supplied to the heat exchanger 16 that takes heat away from the external environment and is again supplied to the pump 32. It has been returned. Moreover, the heat generating part 12A of the magnetic refrigeration unit 12 is provided in the refrigerant flow path on the high temperature side, and heat is transferred from the magnetic body 20 to the refrigerant in the heat generating part 12A. The refrigerant that has passed through the heat generating portion 12A is supplied to the heat exchanger 11 of the magnetic refrigeration cycle, is cooled by the evaporator 2 of the vapor compression refrigeration cycle 1, and is similarly returned to the pump 32.

  The magnetic refrigeration unit 12 shown in FIG. 3 has the structure shown in FIG. 2 such that the magnetic refrigeration refrigerant pipe 44 is not formed in a U shape, and the high temperature part side pipe part 44A and the low temperature part side pipe part 44B are arranged in parallel. This can be realized by configuring. That is, the refrigerant from the pump 14 is branched and supplied to the high temperature part side pipe part 44A and the low temperature part side pipe part 44B, respectively, and the refrigerant from the high temperature part side pipe part 44A and the low temperature part side pipe part 44B is joined again. This is realized by returning to the pump 14. As shown in FIG. 3, when the magnetic body 20 having a positive magnetic effect is incorporated in the magnetic refrigeration unit 12, the magnet device 18 is disposed on the high temperature part side of the magnetic refrigeration cycle 10. When 20 has a negative magnetic effect, the magnet device 18 is disposed on the low temperature part side of the magnetic refrigeration cycle 10 as in the magnetic refrigeration cycle shown in FIGS. 1 and 2.

  In the hybrid magnetic refrigeration apparatus shown in FIG. 3, the refrigerant in the magnetic refrigeration cycle is cooled by the vapor compression refrigeration cycle and further cooled by the magnetic refrigeration cycle, so that cooling at a lower temperature is realized with a high COP. Can do. Since the refrigerant circulating in the magnetic refrigeration cycle is cooled in advance as compared with the case where the same cooling is realized only by the magnetic refrigeration cycle, the magnetic refrigeration apparatus can be made compact.

1 is a block diagram schematically showing a hybrid magnetic refrigeration apparatus according to an embodiment of the present invention. FIG. 2 is a perspective view schematically showing the structure of the magnetic refrigeration unit shown in FIG. 1. It is a block diagram which shows roughly the hybrid type magnetic refrigeration apparatus which concerns on other embodiment of this invention.

Explanation of symbols

  1. . . 1. Vapor compression refrigeration cycle, . . Evaporator, 3. . . Compressor, 4. . . 4. condenser, . . Expansion valve, 6. . . Liquid receiver, 8. . . Heat exchange connection part, 10. . . 10. Magnetic refrigeration cycle, . . Heat exchanger, 12. . . Magnetic refrigeration unit, 12A. . . Exothermic part, 12B. . . Endothermic part, 14. . . Pump, 16. . . Heat exchanger, 18. . . Magnet device, 20. . . Magnetic material, 22. . . Actuator, 24. . . Insulation structure, 42, 44. . . Pipes, 48. . . Cylindrical part, 50. . . permanent magnet

Claims (14)

A compressor for compressing the first refrigerant;
An expansion valve for expanding the first refrigerant;
A condenser for dissipating the heat of the first refrigerant, provided in a flow path of the first refrigerant flowing from the compressor to the expansion valve;
An evaporator provided in the flow path of the first refrigerant flowing from the expansion valve to the compressor, for absorbing heat from the outside by the first refrigerant;
A pump for circulating the second refrigerant;
A magnetic body that generates heat and absorbs heat in accordance with an increase and decrease in the magnetic field;
A magnet for increasing and decreasing the magnetic field on the magnetic body;
A first heat exchanger that is thermally coupled to the evaporator and that cools the second refrigerant by being supplied with the second refrigerant;
An endothermic part that cools the second refrigerant using a magnetic material that absorbs heat due to the increase and decrease of the magnetic field;
A second heat exchanger that cools an object to be cooled by being supplied with the second refrigerant cooled by the heat absorption unit;
Comprising a refrigerator.   2. The refrigerator according to claim 1, further comprising a heat generating unit that heats the second refrigerant using a magnetic material that generates heat due to the increase and decrease of the magnetic field.     The refrigerator according to claim 1, wherein the heat absorption unit cools the second refrigerant cooled by the first heat exchanger.     The refrigerator according to claim 2, wherein the heat generating part is provided adjacent to the first heat exchanger.     5. The refrigerator according to claim 2, wherein the heat generating portion is provided on an upstream side with respect to a direction in which the second refrigerant flows in the first heat exchanger.   The refrigerator according to any one of claims 2, 4, and 5, further comprising a heat insulating structure between the heat generating part and the heat absorbing part. A second refrigerant pipe through which the second refrigerant flows;
The evaporator is provided with a first refrigerant pipe through which the first refrigerant flows,
The refrigerator according to claim 1, wherein the first and second refrigerant pipes are arranged in a nested structure to constitute the first heat exchanger.     The second refrigerant pipe includes a high temperature side portion through which the heated second refrigerant flows and a low temperature side portion through which the cooled second refrigerant flows, and the high temperature side portion and the low temperature side portion are arranged in parallel. The magnetic body is disposed in a cylindrical portion, and the cylindrical portion is disposed in a nested structure so as to penetrate the high temperature side portion and the low temperature side portion of the second refrigerant pipe. The refrigerator according to claim 7, wherein the refrigerator is characterized. A compressor for compressing the first refrigerant;
An expansion valve for expanding the first refrigerant;
A condenser for dissipating the heat of the first refrigerant, provided in a flow path of the first refrigerant flowing from the compressor to the expansion valve;
An evaporator provided in the flow path of the first refrigerant flowing from the expansion valve to the compressor, for absorbing heat from the outside by the first refrigerant;
A pump for circulating the second refrigerant;
A branching portion for branching the second refrigerant from the pump into a first refrigerant flow path provided with the evaporator and a second refrigerant flow path provided with the condenser;
A merge portion that merges the first and second refrigerant flow paths and returns them to the pump;
A magnetic body that generates heat and absorbs heat in accordance with an increase and decrease in the magnetic field;
A magnet for increasing and decreasing the magnetic field on the magnetic body;
A heat-absorbing part that is provided in the first refrigerant flow path and cools the second refrigerant using a magnetic material that absorbs heat due to the increase and decrease of the magnetic field;
A heat generating part that is provided in the second refrigerant flow path and heats the second refrigerant using a magnetic material that generates heat due to the increase and decrease of the magnetic field;
Comprising a refrigerator.     The refrigerator according to claim 9, wherein the heat generating part is provided adjacent to the first heat exchanger.     11. The refrigerator according to claim 9, wherein the heat generating portion is provided on an upstream side with respect to a direction in which the second refrigerant flows in the first heat exchanger.   The refrigerator according to any one of claims 9 to 11, further comprising a heat insulating structure between the heat generating unit and the heat absorbing unit.     The refrigerator according to any one of claims 1 to 12, further comprising an actuator that moves the magnetic body.     The refrigerator according to any one of claims 1 to 13, wherein the compressor includes a piston and moves the magnetic material using the piston operation.

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