Solid-state refrigeration device

Abstract

The solid-state refrigeration device (1) performs a heating operation and a defrosting operation. In the defrosting operation, frost adhering to the second heat exchanger (17) in the heating operation is removed. The solid refrigerant substance (12) includes a plurality of substances (12a-12e) having different temperatures at which the thermal effect is maximum, and the plurality of substances (12a-12e) are arranged along the internal flow path (13) in the order of the temperatures. During the defrosting operation, the conveying direction of the heat medium in the internal flow path (13) is switched to the opposite direction of the heating operation with respect to the phase in which the force field varies.

Description

Technical Field

[0001] The present disclosure relates to a solid-state refrigeration device. Background Art

[0002] The magnetic refrigeration device disclosed in Patent Document 1 has a plurality of beds, a high-temperature side heat exchanger, and a low-temperature side heat exchanger. The beds, the high-temperature side heat exchanger, and the low-temperature side heat exchanger are connected to a heat medium circuit. In the bed, as the magnetic field of the magnetic working medium changes, the magnetic working medium generates heat or absorbs heat. The heat medium of the heat medium circuit is heated by the magnetic working medium that generates heat, or is cooled by the magnetic working medium that absorbs heat. Through such an action, a temperature difference is generated between the heat medium of the high-temperature side heat exchanger and the heat medium of the low-temperature side heat exchanger.

[0003] Since the temperature of the heat medium in the low temperature side heat exchanger decreases, frost may be attached to the surface of the low temperature side heat exchanger. In Patent Document 1, the low temperature side heat exchanger is defrosted by transferring the heat medium stored in the high temperature side heat exchanger to the low temperature side heat exchanger.

[0004] Prior art literature

[0005] Patent Literature

[0006] Patent Document 1: Japanese Patent Publication No. 2016-11799 Summary of the invention

[0007] -Technical problem to be solved by the invention-

[0008] However, according to the defrosting method of Patent Document 1, since the heat medium stored in the high-temperature side heat exchanger is used for defrosting the low-temperature side heat exchanger, in order to ensure sufficient heat energy for melting the frost, the size of the high-temperature side heat exchanger needs to be larger than that of the low-temperature side heat exchanger. In addition, a method of defrosting by replacing the high-temperature side and the low-temperature side by switching the flow path is proposed, but in this method, a valve needs to be added to the heat medium circuit. In addition, a method of storing the heat energy on the high-temperature side and switching the flow path during defrosting, and using the stored heat energy for defrosting is proposed, but in this method, a valve and a tank need to be added to the heat medium circuit.

[0009] An object of the present disclosure is to avoid enlarging and complicating a solid-state refrigeration device such as a magnetic refrigeration device and to enable defrosting of a low-temperature side heat exchanger.

[0010] -Technical solutions to solve technical problems-

[0011] The first aspect of the present disclosure relates to a solid-state refrigeration device 1, which includes: a storage portion 11, a force field modulation portion 15, a first heat exchanger 16, a second heat exchanger 17, a heat medium circuit C, and a heat medium transport portion 21, 50, 100. The storage portion 11 has a solid refrigerant substance 12 and an internal flow path 13, and a heat medium flows in the internal flow path 13 and performs heat exchange with the solid refrigerant substance 12. The force field modulation portion 15 imparts a force field change to the solid refrigerant substance 12 in the storage portion 11 to induce a thermal effect. The first heat exchanger 16, the second heat exchanger 17, and the internal flow path 13 are connected to the heat medium circuit C. The heat medium transport portions 21, 50, 100 transport the heat medium back and forth to the solid refrigerant substance 12 in the storage portion 11 according to the force field change in the heat medium circuit C, and the solid-state refrigeration device 1 performs a heating operation and a defrosting operation. In the heating operation, the heat medium heated by the solid refrigerant substance 12 releases heat in the first heat exchanger 16 and the heat medium cooled by the solid refrigerant substance 12 absorbs heat in the second heat exchanger 17. In the defrosting operation, frost attached to the second heat exchanger 17 in the heating operation is removed. The solid refrigerant substance 12 includes a plurality of substances 12a to 12e with different temperatures having the greatest thermal effect, and the plurality of substances 12a to 12e are arranged in the order of the high and low temperatures along the internal flow path 13. In the defrosting operation, the conveying direction of the heat medium in the internal flow path 13 relative to the phase of the force field change is switched to the opposite direction to that of the heating operation.

[0012] In the first aspect, in the defrosting operation, the conveying direction of the heat medium in the internal flow path 13 relative to the phase of the force field change is switched to the opposite direction to the heating operation. Thus, it is possible to avoid the enlargement of the high-temperature side heat exchanger or the complication of the device structure due to the addition of valves or tanks, and to defrost the low-temperature side heat exchanger.

[0013] According to a second aspect of the present disclosure, based on the first aspect, the storage unit 11 includes a plurality of partial storage units 11a to 11e connected in series in the heat medium circuit C, and each of the plurality of partial storage units 11a to 11e has at least one of the plurality of substances 12a to 12e.

[0014] In the second aspect, the flexibility of the cascade arrangement of the solid refrigerant substance 12 is increased.

[0015] A third aspect of the present disclosure is that, based on the first or second aspect, the force field modulation unit 15 and the heat medium conveying unit 21, 50, 100 are electrically controlled to switch the conveying direction of the heat medium in the internal flow path 13 relative to the phase of the force field change.

[0016] In the third aspect, it is possible to avoid enlarging and complicating the device and to perform defrosting by electrical control.

[0017] A fourth aspect of the present disclosure is, based on the first or second aspect, mechanically controlling the force field modulation unit 15 and the heat medium conveying unit 100 to switch the conveying direction of the heat medium in the internal flow path 13 relative to the phase of the force field variation.

[0018] In the fourth aspect, it is possible to avoid enlarging or complicating the device, and to perform defrosting of the low-temperature side heat exchanger by mechanical control.

[0019] The fifth aspect of the present disclosure is that, based on any one of the first to fourth aspects, the solid-state refrigeration device also includes a fan 17f for supplying air to the second heat exchanger 17, and when the temperature of the second heat exchanger 17 is higher than the ambient temperature of the second heat exchanger 17, the fan 17f is stopped during the defrost operation.

[0020] In the fifth aspect, by stopping the fan 17f when the second heat exchanger 17 is a low-temperature side heat exchanger (e.g., an outdoor heat exchanger) and the temperature of the outdoor heat exchanger is higher than the outdoor air temperature, heat dissipation from the outdoor heat exchanger to the outside air can be prevented, thereby enabling efficient defrosting.

[0021] The sixth aspect of the present disclosure is that, based on any one of the first to fifth aspects, the first heat exchanger 16 is an indoor heat exchanger, and the solid-state refrigeration device also includes an indoor fan 16f for supplying air to the indoor heat exchanger, and the indoor fan 16f is stopped during the defrost operation.

[0022] In the sixth aspect, by stopping the indoor fan 16f during defrosting, it is possible to suppress a decrease in the temperature of the indoor space due to cold air being blown out from the indoor unit provided with the indoor heat exchanger.

[0023] A seventh aspect of the present disclosure is, based on any one of the first to sixth aspects, the frequency of the force field change is increased during the defrosting operation.

[0024] In the seventh aspect, the flow rate of the heat medium increases and the pressure loss increases, and as a result, the amount of heat transferred to the heat medium also increases. In the constituent material of the storage portion 11 and the constituent material of the force field modulation portion 15 close to the material (yoke, etc.), the eddy current loss increases, and as a result, the amount of heat transferred to the heat medium further increases. Therefore, defrosting can be accelerated.

[0025] An eighth aspect of the present disclosure is, based on any one of the first to seventh aspects, wherein during the defrosting operation, a flow rate of the heat medium in the heat medium circuit C is increased.

[0026] In the eighth aspect, the flow rate of the heat medium increases and the pressure loss increases. As a result, the amount of heat transferred to the heat medium also increases, so that the defrosting speed can be increased.

[0027] The ninth aspect of the present disclosure is that, based on any one of the first to eighth aspects, the solid refrigerant substance 12 is a magnetic working medium 12 , and the force field modulation unit 15 is a magnetic field modulation unit 15 that imparts magnetic field changes to the magnetic working medium 12 .

[0028] In the ninth aspect, the magnetic refrigeration device can be quickly started. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Figure 1 is a piping system diagram of a magnetic refrigeration device according to an embodiment;

[0030] Figure 2 is a diagram schematically showing the relationship between the temperature of a plurality of solid refrigerant substances arranged in a cascade shape in a single storage unit and the magnetic refrigeration effect in the magnetic refrigeration device according to the embodiment;

[0031] Figure 3 is a diagram schematically showing the relationship between the temperature of a plurality of solid refrigerant substances arranged in a cascade shape in a plurality of partial storage portions and the magnetic refrigeration effect in the magnetic refrigeration device according to the embodiment;

[0032] Figure 4 is a piping system diagram for explaining a heating operation performed by a magnetic refrigeration device according to an embodiment;

[0033] Figure 5 is a piping system diagram for explaining a defrosting operation performed by a magnetic refrigeration device according to an embodiment;

[0034] Figure 6 is a diagram showing the relationship between magnetic field fluctuations and the heat medium conveyance direction during heating operation performed by the magnetic refrigeration device according to the embodiment;

[0035] Figure 7is a diagram showing the relationship between magnetic field fluctuations and the heat medium conveyance direction during a defrosting operation performed by the magnetic refrigeration device according to the embodiment;

[0036] Figure 8 is a piping system diagram of a magnetic refrigeration device according to Modification 1;

[0037] Fig. 9 is a schematic structural diagram of a magnetic refrigeration unit according to Modification 1;

[0038] Fig.10 is a simplified structural diagram for explaining the operation of the magnetic refrigeration unit described in Modification 1;

[0039] Fig.11 is a simplified structural diagram for explaining the operation of the magnetic refrigeration unit described in Modification 1;

[0040] Fig.12 is a piping system diagram for explaining refrigeration operation in the magnetic refrigeration device according to Modification 1;

[0041] Fig.13 is a piping system diagram for explaining heating operation in the magnetic refrigeration device according to Modification 1;

[0042] Fig.14 is a piping system diagram for explaining a defrosting operation in a magnetic refrigeration device according to Modification 1;

[0043] Fig.15 is a piping system diagram of a magnetic refrigeration device according to Modification 2;

[0044] Fig.16 is a schematic structural diagram of a magnetic refrigeration unit according to Modification 2;

[0045] Fig.17 is a simplified structural diagram for explaining the operation of the magnetic refrigeration unit described in Modification Example 2;

[0046] Fig.18 is a piping system diagram for explaining refrigeration operation in a magnetic refrigeration device according to Modification 2;

[0047] Fig.19 is a piping system diagram for explaining heating operation in the magnetic refrigeration device according to Modification 2;

[0048] Fig. 20 is a piping system diagram for explaining a defrosting operation in a magnetic refrigeration device according to Modification 2;

[0049] Fig.21 is a piping system diagram of a magnetic refrigeration device according to Modification 3;

[0050] Fig. 22 When viewed from the axial direction of the annular housing Fig.21 A top view of a magnetic refrigeration module of the magnetic refrigeration device shown;

[0051] Fig.23 The annular container is viewed from the radial direction. Fig.21 A cross-sectional view of a magnetic refrigeration module of the magnetic refrigeration device shown;

[0052] Fig.24 It is a schematic diagram of the main structure for explaining the mechanical control of the magnetic field modulation unit and the heat medium transport unit in the magnetic refrigeration device according to the modification example 4;

[0053] Fig.25 Observed from outside the valve box Fig.24 A top view of a high-pressure side valve plate of a rotary valve type multi-way reversing valve shown;

[0054] Fig.26 Observed from outside the valve box Fig.24 A top view of a low-pressure side valve plate of a rotary valve type multi-way reversing valve shown;

[0055] Fig. 27 1 is a schematic diagram of an example of a phase adjuster mechanism for mechanically controlling the magnetic field modulation unit 15 in the magnetic refrigeration device according to Modification 5;

[0056] Fig.28 This is a schematic diagram of another example of a phase adjuster mechanism for mechanically controlling the magnetic field modulation unit 15 in the magnetic refrigeration device according to Modification 5;

[0057] Fig.29 This is a piping system diagram of the magnetic refrigeration device involved in Modification Example 6. DETAILED DESCRIPTION

[0058] Hereinafter, embodiments of the present disclosure will be described with reference to the accompanying drawings. It should be noted that the following embodiments are merely preferred examples in nature and are not intended to limit the present invention, its application objects or its scope of use.

[0059] (Implementation Method)

[0060] The embodiment is described. The magnetic refrigeration device 1 of this embodiment is a solid-state refrigeration device that uses the magnetocaloric effect to adjust the temperature of a heat medium, and is applied to, for example, an air conditioning device. In this case, the magnetic refrigeration device 1 adjusts the temperature of the air in the space of the air-conditioning object. The space of the air-conditioning object is, for example, an indoor space. The magnetic refrigeration device 1 switches between heating operation and defrosting operation.

[0061] <Structure of magnetic refrigeration device>

[0062] like Figure 1As shown, the magnetic refrigeration device 1 includes a heat medium circuit C, and a heat medium is filled in the heat medium circuit C. The filled heat medium is transported in the heat medium circuit C. The heat medium includes, for example, a refrigerant, water, brine, and the like.

[0063] The magnetic refrigeration device 1 mainly includes: a storage unit 11, a magnetic field modulation unit 15 as a force field modulation unit, a first heat exchanger 16, a second heat exchanger 17, a reciprocating pump 21 as a heat medium transport unit, and a control unit 30. The storage unit 11, the first heat exchanger 16, the second heat exchanger 17 and the reciprocating pump 21 are connected to each other via a heat medium pipeline to form a heat medium circuit C.

[0064] The storage part 11 has a solid refrigerant substance, namely a magnetic medium 12, and an internal flow path 13. The heat medium flows in the internal flow path 13 and exchanges heat with the solid refrigerant substance 12. The storage part 11 is a hollow shell or column. The storage part 11 is filled with the magnetic medium 12.

[0065] By applying a magnetic field to the magnetic medium 12 or increasing the applied magnetic field, the magnetic medium 12 generates heat. If the magnetic field is removed or the applied magnetic field is weakened, the magnetic medium 12 absorbs heat. As the material of the magnetic medium 12, for example, Gd 5 (Ge 0.5 Si 0.5 ) 4 、La(Fe 1-x Si x ) 13 、La(Fe 1-x Co x Si y ) 13 、La(Fe 1-x Si x ) 13 H y 、Mn(As 0.9 Sb 0.1 )wait.

[0066] For example, Figure 2As shown, the magnetic working medium 12 is composed of a plurality of substances 12a to 12e, and these substances 12a to 12e have different Curie temperatures, and the thermal effect (magnetic refrigeration effect) of these substances 12a to 12e at the Curie temperature is the largest. The various substances 12a to 12e are arranged along the internal flow path 13 in the order of high and low Curie temperatures (i.e., in a cascade shape). Specifically, in the storage portion 11, five magnetic working media 12, namely, a first substance 12a, a second substance 12b, a third substance 12c, a fourth substance 12d, and a fifth substance 12e, are arranged in sequence from the high temperature side to the low temperature side. The Curie temperature of each magnetic working medium 12, that is, the relationship between temperature and magnetic refrigeration effect, is different. In this example, assuming that the Curie temperature of the first substance 12a is Ta, the Curie temperature of the second substance 12b is Tb, the Curie temperature of the third substance 12c is Tc, the Curie temperature of the fourth substance 12d is Td, and the Curie temperature of the fifth substance 12e is Te, then the relationship Ta>Tb>Tc>Td>Te is satisfied.

[0067] exist Figure 2 In the cascade arrangement shown, five magnetic media 12 are arranged in a single receiving portion 11, but the type of material of the magnetic media 12, the structure of the cascade arrangement, etc. are not particularly limited. For example, multiple receiving portions 11 can be arranged in parallel, and the multiple receiving portions 11 respectively have multiple magnetic media 12 arranged in cascade. Or, for example, Figure 3 As shown, the storage section 11 may also be composed of a plurality of partial storage sections 11a to 11e connected in series in the heat medium circuit C, and the plurality of partial storage sections 11a to 11e respectively store corresponding substances among the plurality of substances 12a to 12e. In this case, a single substance may be arranged in all the partial storage sections 11a to 11e, or two or more substances may be arranged in cascade. Alternatively, a single substance may be arranged in one or two or more partial storage sections 11a to 11e, and two or more substances may be arranged in cascade in one or two or more other partial storage sections 11a to 11e. Regardless of the storage section structure, a plurality of substances 12a to 12e are arranged in order of temperature along the internal flow path 13 of the partial storage sections 11a to 11e connected in series.

[0068] The magnetic field modulator 15 imparts magnetic field changes to the magnetic medium 12 in the storage portion 11 to induce a heating effect. The magnetic field modulator 15 is, for example, composed of an electromagnet capable of modulating a magnetic field. The magnetic field modulator 15 performs a first modulation operation and a second modulation operation. In the first modulation operation, a prescribed magnetic field is applied to the magnetic medium 12. In the second modulation operation, a magnetic field smaller than the prescribed magnetic field is applied or the prescribed magnetic field is removed.

[0069] The first heat exchanger 16 may be an indoor heat exchanger that performs heat exchange between the heat medium heated by the magnetic working medium 12 and the indoor air. Alternatively, the first heat exchanger 16 may also perform heat exchange between the heat medium heated by the magnetic working medium 12 and the secondary refrigerant flowing in a utilization unit (e.g., an air handling unit) not shown in the figure. The second heat exchanger 17 may be an outdoor heat exchanger that performs heat exchange between the heat medium cooled by the magnetic working medium 12 and the outdoor air. Alternatively, the second heat exchanger 17 may also perform heat exchange between the heat medium cooled by the magnetic working medium 12 and the secondary refrigerant flowing in a heat source unit (e.g., a cooling tower) not shown in the figure. In the heat medium circuit C, the first heat exchanger 16 and the second heat exchanger 17 are connected via the internal flow path 13 of the storage section 11.

[0070] The reciprocating pump 21 reciprocates to transport the heat medium to the magnetic medium 12 in the storage section 11 according to the change of the magnetic field. The reciprocating pump 21 is composed of a piston pump, for example. The reciprocating pump 21 has a pump housing 22, a piston 23 and a driving mechanism (not shown). The piston 23 is arranged inside the pump housing 22. The piston 23 divides the interior of the pump housing 22 into two chambers. In the heat medium circuit C, one chamber of the pump housing 22 (hereinafter referred to as the first chamber) is connected to the first heat exchanger 16, and the other chamber of the pump housing 22 (hereinafter referred to as the second chamber) is connected to the second heat exchanger 17. The driving mechanism has a rod connected to the piston 23, a crankshaft connected to the rod, and a motor that drives the crankshaft. When the motor drives the crankshaft to rotate, the rod will move forward and backward. In this way, the piston 23 will reciprocate in the pump housing 22.

[0071] Specifically, in the reciprocating pump 21, the first conveying action and the second conveying action are repeatedly and alternately performed. In the first conveying action, the piston 23 moves in a direction that expands the first chamber and shrinks the second chamber. As a result, the heat medium is ejected from the second chamber, and in the heat medium circuit C, the heat medium moves to the second heat exchanger 17, the storage section 11 (internal flow path 13), and the first heat exchanger 16 in sequence, and is sucked into the first chamber. In the second conveying action, the piston 23 moves in a direction that shrinks the first chamber and expands the second chamber. As a result, the heat medium is ejected from the first chamber, and in the heat medium circuit C, the heat medium moves to the first heat exchanger 16, the storage section 11 (internal flow path 13), and the second heat exchanger 17 in sequence, and is sucked into the second chamber.

[0072] The control unit 30 controls the operation of the magnetic field modulation unit 15 and the reciprocating pump 21. The control unit 30 is composed of, for example, a microcomputer and a storage device (specifically, a semiconductor memory) for storing software that causes the microcomputer to operate. The control unit 30 is connected to the magnetic field modulation unit 15 and the reciprocating pump 21 via a communication line.

[0073] <Operation of magnetic refrigeration device>

[0074] The magnetic refrigeration device 1 performs a heat release action (hot blow) and a heat absorption action (cold blow). In the heat release action, by applying a specified magnetic field to the magnetic working medium 12 and causing the heat medium to move in a first direction in the internal flow path 13, the heat medium can be used to transfer the heat energy generated by the magnetic working medium 12 to the outside of the storage part 11, for example, to the first heat exchanger 16, so as to release heat. In the heat absorption action, by applying a magnetic field smaller than the specified magnetic field to the magnetic working medium 12, or removing the specified magnetic field from the magnetic working medium 12, and causing the heat medium to move in a second direction opposite to the first direction in the internal flow path 13, the heat medium can be used to transfer the cold energy generated by the magnetic working medium 12 to the outside of the storage part 11, for example, to the second heat exchanger 17, so as to absorb heat.

[0075] Specifically, if Figure 4 As shown in (a) and (b) of FIG. 1 , in the heat release operation, the first modulation operation (excitation) of the magnetic field modulation unit 15 and the first delivery operation of the reciprocating pump 21 are performed. In the heat release operation, the heat medium is heated in the internal flow path 13 of the storage unit 11. The heated heat medium releases heat in the first heat exchanger 16.

[0076] like Figure 4 As shown in (c) and (d) of FIG. 1 , in the heat absorption operation, the second modulation operation (demagnetization) of the magnetic field modulation unit 15 and the second delivery operation of the reciprocating pump 21 are performed. In the heat absorption operation, the heat medium is cooled in the internal flow path 13 of the storage unit 11. The cooled heat medium absorbs heat in the second heat exchanger 17.

[0077] In the magnetic refrigeration device 1, when the cycle of repeated heat release and heat absorption actions (AMR (Active Magnetic Refrigerator) cycle) described above is performed, the magnetic medium 12 in the storage section 11 generates heat energy and cold energy and regenerates them through changes in the magnetic field, thereby generating a temperature gradient in the storage section 11. As a result, a large temperature difference is generated between the high-temperature end and the low-temperature end of the storage section 11.

[0078] In the case where the first heat exchanger 16 is an indoor heat exchanger and the second heat exchanger 17 is an outdoor heat exchanger, Figure 4 As shown, the heat medium heated by the magnetic medium 12 releases heat to the indoor air in the high-temperature side heat exchanger, i.e., the first heat exchanger 16, and the indoor air is heated. On the other hand, the heat medium cooled by the magnetic medium 12 absorbs heat from the outdoor air in the low-temperature side heat exchanger, i.e., the second heat exchanger 17. Thus, heating operation (heating operation) can be performed.

[0079] During the heating operation, the temperature of the heat medium in the second heat exchanger 17 decreases, so frost may adhere to the surface of the second heat exchanger 17. When a defrost operation is performed to remove the adhered frost, in this embodiment, Figure 5 As shown, the conveying direction of the heat medium in the internal flow path 13 relative to the phase of the magnetic field change is switched to Figure 4 Heating operation is opposite to the direction shown.

[0080] Specifically, in Figure 5 In the actions shown in (a) and (b), the second modulation action (demagnetization) of the magnetic field modulation unit 15 and the first delivery action of the reciprocating pump 21 are performed, and the heat medium cooled in the internal flow path 13 of the storage unit 11 absorbs heat in the first heat exchanger 16. Figure 5 In the actions shown in (c) and (d), the first modulation action (excitation) of the magnetic field modulation unit 15 and the second delivery action of the reciprocating pump 21 are performed, and the heat medium heated in the internal flow path 13 of the storage unit 11 releases heat in the second heat exchanger 17 to perform defrosting.

[0081] Thus, in the defrosting operation of this embodiment, Figure 6 Compared with the heating operation shown in Figure 7 As shown in the figure, the timing of magnetic field fluctuation and heat medium flow, i.e., the AMR (Active Magnetic Refrigerator) cycle, is reversed (phase reversal 180°). Figure 6 , Figure 7 In FIG. 1 , (A) indicates magnetic field fluctuations, and (B) indicates the direction of heat medium transport. Thus, heat is transferred from the high temperature side to the low temperature side, and the low temperature side heat exchanger, that is, the outdoor heat exchanger (second heat exchanger 17), is heated to perform defrosting.

[0082] It should be noted that, in the present embodiment, the case where the internal flow path 13 is arranged along the length direction of the storage section 11, in other words, the case where the high-temperature side inlet and outlet and the low-temperature side inlet and outlet of the internal flow path 13 are arranged at both ends of the length direction of the storage section 11 are described as an example, but the arrangement structure of the internal flow path 13 is not limited to this. For example, the high-temperature side inlet and outlet and the low-temperature side inlet and outlet of the internal flow path 13 may also be arranged on the same surface of the storage section 11. In this case, in the internal flow path 13, the direction in which the heat medium flows from the low-temperature side inlet and outlet to the high-temperature side inlet and outlet is also the "first direction", and the direction in which the heat medium flows from the high-temperature side inlet and outlet to the low-temperature side inlet and outlet is also the "second direction".

[0083] <Features of the embodiment>

[0084] As described above, the magnetic refrigeration device 1 of this embodiment includes a storage part 11, a magnetic field modulation part 15, a first heat exchanger 16, a second heat exchanger 17, a heat medium circuit C and a reciprocating pump 21. The storage part 11 has a magnetic medium 12 and an internal flow path 13, and the heat medium flows in the internal flow path 13 and exchanges heat with the magnetic medium 12. The magnetic field modulation part 15 imparts magnetic field changes to the magnetic medium 12 in the storage part 11 to induce a thermal effect. The first heat exchanger 16, the second heat exchanger 17 and the internal flow path 13 are connected to the heat medium circuit C. The reciprocating pump 21 reciprocates the heat medium relative to the magnetic medium 12 in the storage part 11 according to the magnetic field changes in the heat medium circuit C. The magnetic refrigeration device 1 performs heating operation and defrosting operation. In the heating operation, the heat medium heated by the magnetic medium 12 releases heat in the first heat exchanger 16, and the heat medium cooled by the magnetic medium 12 absorbs heat in the second heat exchanger 17. In the defrosting operation, frost attached to the second heat exchanger 17 in the heating operation is removed. The magnetic medium 12 includes a plurality of substances 12a-12e with different temperatures having the greatest thermal effect, and the plurality of substances 12a-12e are arranged along the internal flow path 13 in the order of the high and low temperatures.

[0085] In the magnetic refrigeration device 1 of this embodiment, during the defrosting operation, the conveying direction of the heat medium in the internal flow path 13 relative to the phase of the magnetic field change is switched to the opposite direction of the heating operation. Thus, it is possible to avoid the enlargement of the high-temperature side heat exchanger or the complication of the device structure due to the addition of valves or tanks, and it is possible to defrost the low-temperature side heat exchanger at a low cost.

[0086] In detail, in the magnetic refrigeration device 1 of the present embodiment, in addition to being able to utilize the heat energy of the first heat exchanger 16 on the high temperature side (in this case, the indoor side) as a heat source, it is also possible to utilize the losses caused by the reversal of the AMR cycle (magnetic refrigeration cycle operation, heat medium pressure loss, eddy current loss, etc.) as a heat source, so there is no need to enlarge the high temperature heat exchanger and / or set up a heat storage tank. Moreover, in the defrosting operation, the temperature of the first heat exchanger 16 (indoor heat exchanger) can be made lower than the temperature of the second heat exchanger 17 (outdoor heat exchanger), and the temperature difference between the two can be utilized as a heat source, so the enlargement of the indoor heat exchanger can be avoided.

[0087] According to the magnetic refrigeration device 1 of the present embodiment, only by electrically controlling the magnetic field modulation unit 15 and the reciprocating pump 21 by the control unit 30, the conveying direction of the heat medium in the internal flow path 13 relative to the phase of the magnetic field change can be switched to the opposite direction of the heating operation during the defrosting operation. Therefore, compared with the existing method of defrosting by using the heat energy generated by the magnetic working medium by switching the flow path by using a valve to replace the high temperature side and the low temperature side during the defrosting operation, the following advantages can be produced. That is, at the moment when the magnetic refrigeration device 1 of the present embodiment is transferred to the defrosting operation, the Curie temperature of each material of the cascade-arranged magnetic working medium 12 is close to the temperature of the heat medium, so the heat transfer amount is increased, so that it is possible to defrost quickly. In contrast, in the existing method of switching the flow path by a valve, at the moment of transferring to the defrosting operation, the Curie temperature of each material of the cascade-arranged magnetic working medium 12 is greatly different from the temperature of the heat medium, so the heat transfer amount becomes small, so that defrosting becomes slow, or defrosting may not be possible.

[0088] In the magnetic refrigeration device 1 of the present embodiment, the storage unit 11 may include a plurality of partial storage units 11a to 11e connected in series in the heat medium circuit C, and each of the plurality of partial storage units 11a to 11e may include at least one of the plurality of substances 12a to 12e. In this way, the flexibility of the cascade arrangement of the solid refrigerant substance 12 is improved.

[0089] In the magnetic refrigeration device 1 of this embodiment, the magnetic field modulation unit 15 and the reciprocating pump 21 can also be electrically controlled to switch the conveying direction of the heat medium in the internal flow path 13 relative to the phase of the magnetic field change. In this way, the enlargement and complexity of the device can be avoided, and defrosting can be performed by electrical control.

[0090] In the magnetic refrigeration device 1 of the present embodiment, the frequency of the magnetic field fluctuation may be increased during the defrosting operation.

[0091] In this way, the frequency of the reciprocating transport of the heat medium increases together with the frequency of the magnetic field change, so the flow rate of the heat medium increases and the pressure loss increases, and as a result, the amount of heat transferred to the heat medium also increases. In the constituent material of the storage part 11 and the constituent material of the force field modulation part 15 close to the material (magnetic yoke, etc.), the eddy current loss increases, and as a result, the amount of heat transferred to the heat medium further increases. Therefore, it is possible to speed up defrosting.

[0092] In the magnetic refrigeration device 1 of the present embodiment, the flow rate of the heat medium in the heat medium circuit C can also be increased during the defrosting operation.

[0093] In this way, the flow rate of the heat medium increases and the pressure loss increases. As a result, the amount of heat transferred to the heat medium also increases, so that the defrosting speed can be increased.

[0094] (Example)

[0095] The defrosting operation of the magnetic refrigeration device 1 of the present embodiment is simulated. The magnetic refrigeration device 1 adopts a structure in which 15 types of magnetic working fluids 12 are arranged in cascade (15-stage cascade AMR). The simulation conditions are: RA (room aircon: indoor air conditioning) 4kW, low-temperature heating (outdoor air temperature: 2°C, indoor temperature: 20°C), 2L of water inside the indoor heat exchanger and pipeline (20°C), 1.4kg of ice in the outdoor heat exchanger (necessary heat of melting 468kJ), and no heat exchange with the indoor air in the indoor heat exchanger (fan stopped). The simulation results are: the ice melts in about 70 seconds, and 3 minutes after the start of defrosting, the temperature of each material of the magnetic working fluid 12 returns to near the Curie temperature before the defrosting operation (i.e., during the heating operation), so that the heating operation can be restarted. It should be noted that if the operation is switched to defrosting, the temperature of each material of the magnetic medium 12 begins to drop, but in the initial stage of operation switching, the temperature of each material is near the Curie temperature, so the amount of heat transfer to the heat medium in the internal flow path 13 is large.

[0096] (Variant 1)

[0097] Modification 1 is described. The magnetic refrigeration device 1 of this modification is a solid-state refrigeration device that uses the magnetocaloric effect to adjust the temperature of a heat medium, and is applied to, for example, an air conditioning device. In this case, the magnetic refrigeration device 1 adjusts the temperature of the air in the space of the air-conditioning object. The space of the air-conditioning object is, for example, an indoor space. The magnetic refrigeration device 1 switches between cooling operation, heating operation, and defrosting operation.

[0098] <Structure of magnetic refrigeration device>

[0099] Figure 8 and Fig. 9 They are respectively a piping system diagram of the magnetic refrigeration device 1 and a structural diagram of the magnetic refrigeration unit U of this modified example. Figure 8 and Fig. 9 In Figure 1 The same components of the magnetic refrigeration device 1 of the embodiment shown are denoted by the same reference numerals.

[0100] like Figure 8 As shown, the magnetic refrigeration device 1 mainly includes a magnetic refrigeration unit U, a first heat exchanger 16, and a second heat exchanger 17. The magnetic refrigeration unit U, the first heat exchanger 16, and the second heat exchanger 17 are connected to each other via a heat medium pipeline to form a heat medium circuit C. It should be noted that, although the illustration is omitted, the magnetic refrigeration device 1 of this variation has a control unit that is the same as the control unit 30 of the embodiment.

[0101] like Fig. 9As shown, the magnetic refrigeration unit U mainly includes: a storage part 11, a force field modulation part, i.e. a magnetic field modulation part 15, a heat medium transportation part, i.e. a reciprocating pump 21, a first outflow pipe 41, a first inflow pipe 42, a second outflow pipe 43, a second inflow pipe 44, a first pump side pipe 45 and a second pump side pipe 46.

[0102] Similar to the above-mentioned embodiment, the storage part 11 has a solid refrigerant substance, namely a magnetic medium 12, and an internal flow path 13, and the heat medium flows in the internal flow path 13 and exchanges heat with the solid refrigerant substance 12. The magnetic medium 12 is composed of a plurality of substances 12a to 12e with different Curie temperatures, and the thermal effect is the largest at the Curie temperature. The plurality of substances 12a to 12e are arranged along the internal flow path 13 in the order of high and low Curie temperatures (i.e., in a cascade shape).

[0103] In this modification, a first internal flow path 13A and a second internal flow path 13B are formed as the internal flow path 13 inside the storage portion 11. A first outflow pipe 41 is connected to one end of the first internal flow path 13A. A second inflow pipe 44 is connected to the other end of the first internal flow path 13A. A first inflow pipe 42 is connected to one end of the second internal flow path 13B. A second outflow pipe 43 is connected to the other end of the second internal flow path 13B.

[0104] A first check valve CV1 is provided on the first outflow pipe 41. A second check valve CV2 is provided on the first inflow pipe 42. A third check valve CV3 is provided on the second outflow pipe 43. A fourth check valve CV4 is provided on the second inflow pipe 44.

[0105] The first check valve CV1 allows the heat medium to flow from the first internal flow path 13A of the storage section 11 to the first heat exchanger 16, and prohibits the heat medium from flowing in the opposite direction. The second check valve CV2 allows the heat medium to flow from the first heat exchanger 16 to the second internal flow path 13B of the storage section 11, and prohibits the heat medium from flowing in the opposite direction. The third check valve CV3 allows the heat medium to flow from the second internal flow path 13B of the storage section 11 to the second heat exchanger 17, and prohibits the heat medium from flowing in the opposite direction. The fourth check valve CV4 allows the heat medium to flow from the second heat exchanger 17 to the first internal flow path 13A of the storage section 11, and prohibits the heat medium from flowing in the opposite direction.

[0106] The magnetic field modulator 15, similarly to the above-described embodiment, imparts magnetic field changes to the magnetic medium 12 in the storage portion 11 to induce a heating effect. The magnetic field modulator 15 is, for example, composed of an electromagnet capable of modulating a magnetic field. The magnetic field modulator 15 performs a first modulation operation and a second modulation operation. In the first modulation operation, a prescribed magnetic field is applied to the magnetic medium 22. In the second modulation operation, a magnetic field smaller than the prescribed magnetic field is applied or the prescribed magnetic field is removed.

[0107] The reciprocating pump 21 reciprocates and transports the heat medium of the heat medium circuit C, similarly to the above-described embodiment. The reciprocating pump 21 is composed of a piston pump. The reciprocating pump 21 includes a pump housing 22, a piston 23, and a drive mechanism (not shown). The piston 23 is arranged inside the pump housing 22. The piston 23 divides the inside of the pump housing 22 into two chambers. The reciprocating pump 21 is provided with a first port 24 and a second port 25. One chamber of the pump housing 22 is connected to the first port 24, and the other chamber is connected to the second port 25.

[0108] One end of the first pump side pipe 45 is connected to the first port 24. The other end of the first pump side pipe 45 is connected to the upstream side of the second check valve CV2 in the first inflow pipe 42. One end of the second pump side pipe 46 is connected to the second port 25. The other end of the second pump side pipe 46 is connected to the upstream side of the fourth check valve CV4 in the second inflow pipe 44.

[0109] The driving mechanism includes a rod connected to the piston 23, a crankshaft connected to the rod, and a motor driving the crankshaft. When the motor drives the crankshaft to rotate, the rod moves forward and backward. In this way, the piston 23 reciprocates in the pump housing 22.

[0110] Specifically, in the reciprocating pump 30, the first conveying operation and the second conveying operation are repeatedly and alternately performed. Fig.10 , Fig.11 In (A)), the piston 23 moves toward the first port 24. As a result, the heat medium is ejected from the first port 24. The ejected heat medium flows through the first inlet pipe 42, the second internal flow path 13B, and the second outlet pipe 43 in sequence. Fig.10 , Fig.11 In (B), the piston 23 moves toward the second port 25. As a result, the heat medium is ejected from the second port 25. The ejected heat medium flows through the second inlet pipe 44, the first internal flow path 13A, and the first outlet pipe 41 in sequence.

[0111] <Operation of magnetic refrigeration device>

[0112] The magnetic refrigeration device 1 of this variant performs cooling operation, heating operation and defrosting operation. In this variant, the first heat exchanger 16 is an indoor heat exchanger that exchanges heat between the heat medium heated by the magnetic working medium 12 and the indoor air, and the second heat exchanger 17 is an outdoor heat exchanger that exchanges heat between the heat medium cooled by the magnetic working medium 12 and the outdoor air. That is, in cooling operation, the air in the indoor space is cooled. Cooling operation corresponds to cooling operation. In heating operation, the air in the indoor space is heated. Heating operation corresponds to heating operation. In defrosting operation, the frost attached to the outdoor heat exchanger will melt.

[0113] During cooling operation, Fig.10 The action shown in (A) and Fig.10 The action shown in (B).

[0114] exist Fig.10 In the action shown in (A), the first modulation action of the magnetic field modulation unit 15 and the first delivery action of the reciprocating pump 21 are performed simultaneously. As a result, the heat medium is heated in the second internal flow path 13B of the storage unit 11, and the heated heat medium flows out from the second outflow pipe 43. At the same time, the heat medium in the heat medium circuit C flows into the second port 25 of the pump housing 22.

[0115] exist Fig.10 In the action shown in (B), the second modulation action of the magnetic field modulation unit 15 and the second delivery action of the reciprocating pump 21 are performed simultaneously. As a result, the heat medium is cooled in the first internal flow path 13A of the storage unit 11, and the cooled heat medium flows out from the first outflow pipe 41. At the same time, the heat medium in the heat medium circuit C flows into the first port 24 of the pump housing 22.

[0116] exist Fig.10 In the operation shown in (A), the heat medium heated by the magnetic refrigeration unit U is as follows Fig.12 As shown in FIG. 1 , the heat medium flows in the second heat exchanger 17. In the second heat exchanger 17, that is, in the outdoor heat exchanger, the heat medium releases heat to the outdoor air. The heat medium after releasing heat in the second heat exchanger 17 returns to the magnetic refrigeration unit U.

[0117] exist Fig.10 In the operation shown in (B), the heat medium cooled by the magnetic refrigeration unit U is as follows: Fig.12 As shown in FIG. 1 , the heat medium flows in the first heat exchanger 16. In the first heat exchanger 16, that is, in the indoor heat exchanger, the heat medium absorbs heat from the indoor air. As a result, the indoor air is cooled. The heat medium after absorbing heat in the first heat exchanger 16 returns to the magnetic refrigeration unit U.

[0118] It should be noted that for convenience, Fig.12 In the figure, the flow of the heat medium in each operation is shown in the same figure. Fig.12 In the figure, the heat exchangers for releasing heat from the heat medium in the first heat exchanger 16 and the second heat exchanger 17 are shaded, and the heat exchangers for absorbing heat from the heat medium are circled. Fig.13 and Fig.14 The same is true in China.

[0119] In heating operation, the Fig.11 The action shown in (A) and Fig.11 The action shown in (B).

[0120] exist Fig.11 In the action shown in (A), the second modulation action of the magnetic field modulation unit 15 and the first delivery action of the reciprocating pump 21 are performed simultaneously. As a result, the heat medium is cooled in the second internal flow path 13B of the storage unit 11, and the cooled heat medium flows out from the second outflow pipe 43. At the same time, the heat medium in the heat medium circuit C flows into the second port 25 of the pump housing 22.

[0121] exist Fig.11 In the action shown in (B), the first modulation action of the magnetic field modulation unit 15 and the second delivery action of the reciprocating pump 21 are performed simultaneously. As a result, the heat medium is heated in the first internal flow path 13A of the storage unit 11, and the heated heat medium flows out from the first outflow pipe 41. At the same time, the heat medium in the heat medium circuit C flows into the first port 24 of the pump housing 22.

[0122] exist Fig.11 In the operation shown in (A), the heat medium cooled by the magnetic refrigeration unit U is as follows Fig.13 As shown in FIG. 1 , the heat medium flows in the second heat exchanger 17. In the second heat exchanger 17, that is, in the outdoor heat exchanger, the heat medium absorbs heat from the outdoor air. The heat medium after absorbing heat in the second heat exchanger 17 returns to the magnetic refrigeration unit U.

[0123] exist Fig.11 In the operation shown in (B), the heat medium heated by the magnetic refrigeration unit U is as follows Fig.13 As shown in FIG. 1 , the heat medium flows in the first heat exchanger 16. In the first heat exchanger 16, that is, in the indoor heat exchanger, the heat medium releases heat to the indoor air. As a result, the indoor air is heated. The heat medium after releasing heat in the first heat exchanger 16 returns to the magnetic refrigeration unit U.

[0124] In the defrosting operation, the action is basically the same as that in the cooling operation, that is, Fig.10 The action shown in (A) and Fig.10 The action shown in (B) is repeated alternately.

[0125] exist Fig.10 In the operation shown in (A), the heat medium heated by the magnetic refrigeration unit U is as follows Fig.14 As shown in FIG. 1 , the heat medium flows in the second heat exchanger 17. In the second heat exchanger 17, that is, in the outdoor heat exchanger, the frost on the surface of the outdoor heat exchanger is melted by the heat medium flowing in the interior thereof. The heat medium used to defrost the outdoor heat exchanger returns to the magnetic refrigeration unit U.

[0126] exist Fig.10 In the operation shown in (B), the heat medium cooled by the magnetic refrigeration unit U is as follows: Fig.14As shown in FIG. 1 , the heat medium flows in the first heat exchanger 16. In the first heat exchanger 16, that is, in the indoor heat exchanger, the heat medium absorbs heat from the indoor air. The heat medium after absorbing heat in the first heat exchanger 16 returns to the magnetic refrigeration unit U.

[0127] <Features of Modification 1>

[0128] As described above, in the magnetic refrigeration device 1 of this modification, similarly to the above-described embodiment, in the defrosting operation, the conveying direction of the heat medium in the internal flow path 13 relative to the phase of the magnetic field change is switched to the opposite direction to the heating operation. Thus, it is possible to avoid the enlargement of the high-temperature side heat exchanger or the complication of the device structure due to the addition of valves or tanks, and it is possible to defrost the low-temperature side heat exchanger at a low cost.

[0129] (Variant 2)

[0130] Modification 2 is described. The magnetic refrigeration device 1 of this modification is a solid-state refrigeration device that uses the magnetocaloric effect to adjust the temperature of a heat medium, and is applied to, for example, an air conditioning device. In this case, the magnetic refrigeration device 1 adjusts the temperature of the air in the space of the air-conditioning object. The space of the air-conditioning object is, for example, an indoor space. The magnetic refrigeration device 1 switches between cooling operation, heating operation, and defrosting operation.

[0131] <Structure of magnetic refrigeration device>

[0132] Fig.15 and Fig.16 They are respectively a piping system diagram of the magnetic refrigeration device 1 and a structural diagram of the magnetic refrigeration unit U of this modified example. Fig.15 and Fig.16 In Figure 1 The same components of the magnetic refrigeration device 1 of the embodiment shown are denoted by the same reference numerals.

[0133] like Fig.15 As shown, the magnetic refrigeration device 1 mainly includes a magnetic refrigeration unit U, a first heat exchanger 16, a second heat exchanger 17, a first four-way reversing valve F1, and a second four-way reversing valve F2. The magnetic refrigeration unit U, the first heat exchanger 16, and the second heat exchanger 17 are connected to each other via a heat medium pipeline to form a heat medium circuit C. It should be noted that, although the illustration is omitted, the magnetic refrigeration device 1 of this modified example has the same control mechanism as the control unit 30 of the embodiment.

[0134] like Fig.16As shown, the magnetic refrigeration unit U includes two magnetic refrigeration modules 10 as solid-state refrigeration modules, a low-temperature outflow pipe 51, a low-temperature inflow pipe 52, a high-temperature outflow pipe 53, a high-temperature inflow pipe 54, and a unit side pump 55. The magnetic refrigeration unit U has a low-temperature first three-way valve 56, a low-temperature second three-way valve 57, a high-temperature first three-way valve 58, and a high-temperature second three-way valve 59. The two magnetic refrigeration modules 10 are composed of a first magnetic refrigeration module 10A and a second magnetic refrigeration module 10B. In this variant, the heat medium transport unit 50 is composed of a unit side pump 55 and a plurality of three-way valves 56, 57, 58, and 59.

[0135] The first magnetic refrigeration module 10A and the second magnetic refrigeration module 10B each include a storage portion 11 and a force field modulation portion, that is, a magnetic field modulation portion 15 .

[0136] Similar to the above-mentioned embodiment, the storage part 11 has a solid refrigerant substance, namely a magnetic medium 12, and an internal flow path 13, and the heat medium flows in the internal flow path 13 and exchanges heat with the solid refrigerant substance 12. The magnetic medium 12 is composed of a plurality of substances 12a to 12e with different Curie temperatures, and the thermal effect is the largest at the Curie temperature. The plurality of substances 12a to 12e are arranged along the internal flow path 13 in the order of high and low Curie temperatures (i.e., in a cascade shape).

[0137] The magnetic field modulator 15, similarly to the above-described embodiment, imparts magnetic field changes to the magnetic medium 12 in the storage portion 11 to induce a heating effect. The magnetic field modulator 15 is, for example, composed of an electromagnet capable of modulating a magnetic field. The magnetic field modulator 15 performs a first modulation operation and a second modulation operation. In the first modulation operation, a prescribed magnetic field is applied to the magnetic medium 22. In the second modulation operation, a magnetic field smaller than the prescribed magnetic field is applied or the prescribed magnetic field is removed.

[0138] A first internal flow path 13A and a second internal flow path 13B are respectively formed inside the storage part 11 of each magnetic refrigeration module 10. The low-temperature end of the first internal flow path 13A of the first magnetic refrigeration module 10A is connected to the low-temperature outflow pipe 51 via the low-temperature first three-way valve 56. The low-temperature end of the second internal flow path 13B of the first magnetic refrigeration module 10A is connected to the low-temperature inflow pipe 52 via the low-temperature second three-way valve 57. The high-temperature end of the first internal flow path 13A of the second magnetic refrigeration module 10B is connected to the high-temperature inflow pipe 54 via the high-temperature second three-way valve 59. The high-temperature end of the second internal flow path 13B of the second magnetic refrigeration module 10B is connected to the high-temperature inflow pipe 53 via the high-temperature first three-way valve 58.

[0139] The unit side pump 55 is provided on the high temperature outflow pipe 53. The unit side pump 55 is a one-way pump. The unit side pump 55 delivers the heat medium to the downstream side of the high temperature outflow pipe 53.

[0140] The first valve port of the low-temperature first three-way valve 56 is connected to the low-temperature outflow pipe 51. The second valve port of the low-temperature first three-way valve 56 is connected to the low-temperature end of the first internal flow path 13A of the second magnetic refrigeration module 10B. The third valve port of the low-temperature first three-way valve 56 is connected to the low-temperature end of the first internal flow path 13A of the first magnetic refrigeration module 10A.

[0141] The first valve port of the low-temperature second three-way valve 57 is connected to the low-temperature inflow pipe 52. The second valve port of the low-temperature second three-way valve 57 is connected to the low-temperature end of the second internal flow path 13B of the second magnetic refrigeration module 10B. The third valve port of the low-temperature second three-way valve 57 is connected to the low-temperature end of the second internal flow path 13B of the first magnetic refrigeration module 10A.

[0142] The first valve port of the high temperature first three-way valve 58 is connected to the high temperature outflow pipe 53. The second valve port of the high temperature first three-way valve 58 is connected to the high temperature end of the second internal flow path 13B of the second magnetic refrigeration module 10B. The third valve port of the high temperature first three-way valve 58 is connected to the high temperature end of the second internal flow path 13B of the first magnetic refrigeration module 10A.

[0143] The first valve port of the high-temperature second three-way valve 59 is connected to the high-temperature inflow pipe 54. The second valve port of the high-temperature second three-way valve 59 is connected to the high-temperature end of the first internal flow path 13A of the second magnetic refrigeration module 10B. The third valve port of the high-temperature second three-way valve 59 is connected to the high-temperature end of the first internal flow path 13A of the first magnetic refrigeration module 10A.

[0144] Each of the three-way valves 56, 57, 58, and 59 has a first valve port, a second valve port, and a third valve port. It should be noted that in the accompanying drawings, the first valve port of the three-way valve is represented by a symbol with a circled number 1, the second valve port of the three-way valve is represented by a symbol with a circled number 2, and the third valve port of the three-way valve is represented by a symbol with a circled number 3.

[0145] Each of the three-way valves 56, 57, 58, 59 is in the first state ( Fig.16 The solid line shows the state) and the second state ( Fig.16 Each three-way valve 56, 57, 58, 59 in the first state connects the first valve port with the second valve port. Each three-way valve 56, 57, 58, 59 in the second state connects the first valve port with the third valve port.

[0146] In this modification, Fig.15 The first heat exchanger 16 shown is an indoor heat exchanger for exchanging heat between the heat medium and the indoor air. One end of the indoor heat exchanger 16 is connected to the second valve port of the first four-way reversing valve F1 via a pipeline. The other end of the first heat exchanger 16 is connected to the second valve port of the second four-way reversing valve F2 via a pipeline. Fig.15The second heat exchanger 17 shown is an outdoor heat exchanger that serves as a heat source. The second heat exchanger 17 exchanges heat between the heat medium and the outdoor air. One end of the second heat exchanger 17 is connected to the third valve port of the first four-way reversing valve F1 via a pipe. The other end of the second heat exchanger 17 is connected to the third valve port of the second four-way reversing valve F2 via a pipe.

[0147] The first four-way reversing valve F1 and the second four-way reversing valve F2 are switching mechanisms for switching the flow path of the heat medium in the heat medium circuit C. The first four-way reversing valve F1 and the second four-way reversing valve F2 of this modified example switch the flow path of the heat medium in the cooling operation, heating operation and defrosting operation. Each of the four-way reversing valves F1 and F2 has a first valve port, a second valve port, a third valve port and a fourth valve port, respectively. It should be noted that in the accompanying drawings, the first valve port of the four-way reversing valve is represented by a symbol with a circled number 1, the second valve port of the four-way reversing valve is represented by a symbol with a circled number 2, the third valve port of the four-way reversing valve is represented by a symbol with a circled number 3, and the fourth valve port of the four-way reversing valve is represented by a symbol with a circled number 4.

[0148] Each of the four-way reversing valves F1, F2 is in the first state ( Fig.15 The state shown by the solid line) and the second state ( Fig.15 Each four-way reversing valve F1, F2 in the first state connects the first valve port with the second valve port and connects the third valve port with the fourth valve port. Each four-way reversing valve F1, F2 in the second state connects the first valve port with the third valve port and connects the second valve port with the fourth valve port.

[0149] The first valve port of the first four-way reversing valve F1 is connected to the high temperature inflow pipe 54. The second valve port of the first four-way reversing valve F1 is connected to the first heat exchanger 16. The third valve port of the first four-way reversing valve F1 is connected to the second heat exchanger 17. The fourth valve port of the first four-way reversing valve F1 is connected to the low temperature inflow pipe 52.

[0150] The first valve port of the second four-way reversing valve F2 is connected to the high-temperature outflow pipe 53. The second valve port of the second four-way reversing valve F2 is connected to the first heat exchanger 16. The third valve port of the second four-way reversing valve F2 is connected to the second heat exchanger 17. The fourth valve port of the second four-way reversing valve F2 is connected to the low-temperature outflow pipe 51.

[0151] It should be noted that the control unit 30 of this modification is connected to the magnetic refrigeration unit U and the four-way reversing valves F1 and F2 via a communication line. In other words, the control unit 30 controls the magnetic field modulation unit 15, the heat medium transport unit 50 and the four-way reversing valves F1 and F2 respectively.

[0152] <Operation of magnetic refrigeration device>

[0153] The magnetic refrigeration device 1 of this variant performs cooling operation, heating operation and defrosting operation. In this variant, the first heat exchanger 16 is an indoor heat exchanger that exchanges heat between the heat medium heated by the magnetic working medium 12 and the indoor air, and the second heat exchanger 17 is an outdoor heat exchanger that exchanges heat between the heat medium cooled by the magnetic working medium 12 and the outdoor air. That is, in cooling operation, the air in the indoor space is cooled. Cooling operation corresponds to cooling operation. In heating operation, the air in the indoor space is heated. Heating operation corresponds to heating operation. In defrosting operation, the frost attached to the outdoor heat exchanger will melt.

[0154] During cooling operation, Fig.17 The action shown in (A) and Fig.17 The switching cycle of each action is about 1 second.

[0155] exist Fig.17 In the action shown in (A), the first magnetic refrigeration module 10A performs the first modulation action, and the second magnetic refrigeration module 10B performs the second modulation action. The low-temperature first three-way valve 56 is set to the first state, the low-temperature second three-way valve 57 is set to the second state, the high-temperature first three-way valve 58 is set to the second state, and the high-temperature second three-way valve 59 is set to the first state. The unit side pump 55 is operated.

[0156] exist Fig.17 In the action shown in (B), the first magnetic refrigeration module 10A performs the second modulation action, and the second magnetic refrigeration module 10B performs the first modulation action. The low-temperature first three-way valve 56 is set to the second state, the low-temperature second three-way valve 57 is set to the first state, the high-temperature first three-way valve 58 is set to the first state, and the high-temperature second three-way valve 59 is set to the second state. The unit side pump 55 is operated.

[0157] like Fig.18 As shown, in the cooling operation, the first four-way reversing valve F1 is set to the second state, and the second four-way reversing valve F2 is set to the second state. Thus, "the heat medium cooled by each magnetic refrigeration module 10 flows through the low-temperature outflow pipe 51, the first heat exchanger 16 and the low-temperature inflow pipe 52, and the heat medium heated by each magnetic refrigeration module 10 flows through the high-temperature outflow pipe 53, the second heat exchanger 17 and the high-temperature inflow pipe 54". It should be noted that for convenience, in Fig.18 In FIG. 1 , the flow of the heat medium in each operation is shown in the same figure. Fig.18 In the figure, the heat exchangers for releasing heat from the heat medium in the first heat exchanger 16 and the second heat exchanger 17 are shaded, and the heat exchangers for absorbing heat from the heat medium are circled. Fig.19 and Fig. 20 The same is true in China.

[0158] Specifically, the heat medium heated by the magnetic refrigeration unit U passes through the second four-way reversing valve F2 and flows in the second heat exchanger 17. In the second heat exchanger 17, that is, in the outdoor heat exchanger, the heat medium releases heat to the outdoor air. The heat medium after releasing heat in the second heat exchanger 17 returns to the magnetic refrigeration unit U through the first four-way reversing valve F1.

[0159] The heat medium cooled by the magnetic refrigeration unit U passes through the second four-way reversing valve F2 and flows in the first heat exchanger 16. In the first heat exchanger 16, that is, in the indoor heat exchanger, the heat medium absorbs heat from the indoor air. As a result, the indoor air is cooled. The heat medium that absorbs heat in the first heat exchanger 16 returns to the magnetic refrigeration unit U through the first four-way reversing valve F1.

[0160] During heating operation, the Fig.17 The action shown in (A) and Fig.17 The action shown in (B). Fig.19 As shown, in the heating operation, the first four-way reversing valve F1 is set to the first state, and the second four-way reversing valve F2 is set to the first state. Thus, a flow path is formed in which the heat medium heated by each magnetic refrigeration module 10 flows through the high-temperature outflow pipe 53, the first heat exchanger 16, and the high-temperature inflow pipe 54, and the heat medium cooled by each magnetic refrigeration module 10 flows through the low-temperature outflow pipe 51, the second heat exchanger 17, and the low-temperature inflow pipe 52.

[0161] Specifically, the heat medium cooled by the magnetic refrigeration unit U passes through the second four-way reversing valve F2 and flows in the second heat exchanger 17. In the second heat exchanger 17, that is, in the outdoor heat exchanger, the heat medium absorbs heat from the outdoor air. The heat medium that absorbs heat in the second heat exchanger 17 returns to the magnetic refrigeration unit U through the first four-way reversing valve F1.

[0162] The heat medium heated by the magnetic refrigeration unit U passes through the second four-way reversing valve F2 and flows in the first indoor heat exchanger 16. In the first indoor heat exchanger 16, that is, in the indoor heat exchanger, the heat medium releases heat to the indoor air. As a result, the indoor air is heated. The heat medium after releasing heat in the first indoor heat exchanger 16 returns to the magnetic refrigeration unit U through the first four-way reversing valve F1.

[0163] In the defrosting operation, the same operation as in the cooling operation is performed. That is, in the defrosting operation, the cooling operation is repeated alternately. Fig.17 The action shown in (A) and Fig.17The switching cycle of each action is about 1 second. The defrosting operation is performed when the conditions for frost to form on the surface of the second heat exchanger 17, that is, the outdoor heat exchanger, are met, for example, during the heating operation in winter.

[0164] like Fig. 20 As shown, in the defrosting operation, the first four-way reversing valve F1 is set to the second state, and the second four-way reversing valve F2 is set to the second state. Thus, a flow path is formed in which the heat medium cooled by each magnetic refrigeration module 10 flows through the low-temperature outflow pipe 51, the first heat exchanger 16, and the low-temperature inflow pipe 52, and the heat medium heated by each magnetic refrigeration module 10 flows through the high-temperature outflow pipe 53, the second heat exchanger 17, and the high-temperature inflow pipe 54.

[0165] Specifically, the heat medium heated by the magnetic refrigeration unit U passes through the second four-way reversing valve F2 and flows in the second heat exchanger 17. In the second heat exchanger 17, that is, in the outdoor heat exchanger, the frost on the surface of the outdoor heat exchanger is melted by the heat medium flowing inside it. The heat medium used to defrost the outdoor heat exchanger returns to the magnetic refrigeration unit U through the first four-way reversing valve F1.

[0166] The heat medium cooled by the magnetic refrigeration unit U passes through the second four-way reversing valve F2 and flows in the first heat exchanger 16. In the first heat exchanger 16, that is, in the indoor heat exchanger, the heat medium absorbs heat from the indoor air. The heat medium after absorbing heat in the first heat exchanger 16 returns to the magnetic refrigeration unit U through the first four-way reversing valve F1.

[0167] <Features of Modification 2>

[0168] When cooling operation is not required, Fig.19 The piping system shown in the figure adopts a structure without four-way reversing valves F1 and F2. In the defrosting operation, the magnetic field modulation unit 15 and the heat medium conveying unit 50 are electrically controlled, thereby Fig.17 The actions shown in (A) and (B) of the embodiment switch the conveying direction of the heat medium in the internal flow path 13 relative to the phase of the magnetic field change to the opposite direction of the heating operation (heating operation). This can avoid the large-scale heat exchanger on the high temperature side or the complication of the device structure due to the addition of valves or tanks, and can defrost the heat exchanger on the low temperature side at a low cost.

[0169] (Variant 3)

[0170] Modification 3 is described. The magnetic refrigeration device 1 of this modification is a solid-state refrigeration device that uses magnetocaloric effect to adjust the temperature of a heat medium, and is applied to, for example, an air conditioning device. In this case, the magnetic refrigeration device 1 adjusts the temperature of the air in the space of the air conditioning target. The space of the air conditioning target is, for example, an indoor space.

[0171] <Structure of magnetic refrigeration device>

[0172] In the magnetic refrigeration device 1 of the embodiment and variants 1 and 2, a magnetic medium 12 is filled in a storage portion 11 formed of a hollow shell or a column, and a magnetic field modulation portion 15 formed of an electromagnet capable of modulating the magnetic field is used to impart a magnetic field change to the magnetic medium 12 in the storage portion 11.

[0173] In contrast, the magnetic refrigeration device 1 of this modified example is a magnetic heat pump device with a magnetic circuit rotation method. Fig.21 As shown, the magnetic refrigeration device 1 of this modified example mainly includes a heat medium circuit C provided with a magnetic refrigeration module 10, a first heat exchanger 16, a second heat exchanger 17, and a heat medium pump 21A. The components of the heat medium circuit C are connected to each other via a heat medium pipeline. The magnetic refrigeration device 1 is a solid-state refrigeration device that uses a thermal effect to adjust the temperature of a heat medium, and the magnetic refrigeration module 10 is a solid-state refrigeration module that uses a thermal effect to adjust the temperature of a heat medium.

[0174] The magnetic refrigeration module 10 is, for example, provided in an air conditioning device that performs heat exchange with a secondary refrigerant, air, etc. The use of the magnetic refrigeration module 10 is not limited thereto, and for example, it may be provided in a magnetic refrigeration system 1 configured as a cooling air device dedicated to refrigeration.

[0175] The magnetic refrigeration module 10 includes an annular receiving portion 11 having a plurality of partial receiving portions 11a to 11l, wherein the plurality of partial receiving portions 11a to 11l receive a magnetic medium 12 as a solid refrigerant substance and form an internal flow path 13 for the flow of a heat medium. The magnetic refrigeration module 10 generates a magnetocaloric effect by applying a magnetic field as a force field to the magnetic medium 12 or removing a magnetic field as a force field from the magnetic medium 12, thereby heating or cooling the heat medium flowing in the flow path 13.

[0176] In this variation, the magnetic working medium 12 is also composed of a plurality of substances 12a-12e having different Curie temperatures. The thermal effect is greatest at the Curie temperature. The plurality of substances 12a-12e are arranged in order of Curie temperatures (i.e., in a cascade shape) along the internal flow path 13 of each partial storage portion 11a-11l.

[0177] like Fig.21 and Fig. 22As shown, the magnetic refrigeration module 10 is composed of a plurality of, for example, 12 unit modules 10a to 101. The constituent elements of the plurality of unit modules 10a to 101 are respectively stored in a plurality of partial storage sections 11a to 111. In the present embodiment, each partial storage section 11a to 111 is, for example, an annular sector, but is not limited thereto, and may also be a sector or a trapezoid. A plurality of partial storage sections 11a to 111 are combined into an annular shape to form the annular storage section 11 of the magnetic refrigeration module 10. The thickness of each partial storage section 11a to 111 is set to a thickness that is not prone to magnetic flux leakage and can ensure the volume of the necessary storage section. It should be noted that in the following description, when describing the partial storage section 11a, it means any storage section sheet among the plurality of partial storage sections 11a to 111, and when describing the unit module 10a, it means any unit module among the plurality of unit modules 10a to 101.

[0178] In this variation, if Fig. 22 and Fig.23 As shown, a force field modulation part, namely a magnetic field modulation part 15, is arranged in the axial direction of the annular storage part 11 in a manner of sandwiching the magnetic refrigeration module 10. The magnetic field modulation part 15 has: a force field generating part, namely an annular magnet 15a, arranged close to the magnetic refrigeration module 10; a yoke 15b for supporting the annular magnet 15a and forming a magnetic circuit; and a rotating mechanism 15c. The rotating mechanism 15c is arranged in a manner of penetrating the central opening of the magnetic refrigeration module 10 and extending in the axial direction of the annular storage part 11. The magnet 15a rotates in the circumferential direction of the annular storage part 11 through the rotating mechanism 15c. The number of magnets 15a (a pair of magnets sandwiching the magnetic refrigeration module 10 in the axial direction of the annular storage part 11) arranged is equal to the number of poles of the magnetic circuit. In this example, two magnets 15a are arranged, and the magnets 15a overlap the area of ​​three partial storage parts 11a. In this example, the magnets 15a and the unit modules 20a are evenly arranged in the coaxial circumferential direction. The annular housing portion 11, namely the magnetic refrigeration module 10, can be fixed.

[0179] In the magnetic refrigeration module 10 of this modified example, as the rotating mechanism 15c rotates, the unit module 10a excited by the magnet 15a changes all the time, thus constituting a magnetic refrigeration module 10 of a magnet rotating type. It should be noted that, Fig.21 and Fig. 22 The state in which the unit modules 10a, 10b, 10c, 10g, 10h, and 10i are excited and the unit modules 10d, 10e, 10f, 10j, 10k, and 101 are demagnetized is shown.

[0180] like Fig.21As shown, each unit module 10a~101 constituting the magnetic refrigeration module 10 has a low-temperature side inflow path 61, a low-temperature side outflow path 62, a high-temperature side inflow path 63, and a high-temperature side outflow path 64. Each inflow path 61, 63 and each outflow path 62, 64 is connected to the internal flow path 13 of the partial storage section 11a~11l of each unit module 10a~10l. The heat medium flowing in from the low-temperature side inflow path 61 flows through the internal flow path 13 of the partial storage section 11a and is discharged from the high-temperature side outflow path 64. The heat medium flowing in from the high-temperature side inflow path 63 flows through the internal flow path 13 of the partial storage section 11a and is discharged from the low-temperature side outflow path 62.

[0181] In this modification, the first heat exchanger 16 is an indoor heat exchanger that exchanges heat between the heat medium heated in the magnetic refrigeration module 10 and the indoor air. The first heat exchanger 16 has a first outflow portion 16a connected to the high-temperature side inflow path 63 of the magnetic refrigeration module 10 and a first inflow portion 16b connected to the high-temperature side outflow path 64 of the magnetic refrigeration module 10. A high-pressure side multi-way reversing valve 110 is provided on the heat medium pipeline between the first outflow portion 16a and the high-temperature side inflow path 63 of each unit module 10a~10l. A low-pressure side multi-way reversing valve 120 is provided on the heat medium pipeline between the first inflow portion 16b and the high-temperature side outflow path 64 of each unit module 10a~10l. In this modification, the high-pressure side multi-way reversing valve 110 and the low-pressure side multi-way reversing valve 120 are formed as one body to constitute a rotary valve type multi-way reversing valve 100.

[0182] In this variation, the second heat exchanger 17 is an outdoor heat exchanger that exchanges heat between the heat medium cooled in the magnetic refrigeration module 10 and the outdoor air. The second heat exchanger 17 has a second outflow portion 17a connected to the low-temperature side inflow path 61 of the magnetic refrigeration module 10 and a second inflow portion 17b connected to the low-temperature side outflow path 62 of the magnetic refrigeration module 10. A first check valve 91 is provided on the heat medium pipeline between the second outflow portion 17a and the low-temperature side inflow path 61 of each unit module 10a to 101. A second check valve 92 is provided on the heat medium pipeline between the second inflow portion 17b and the low-temperature side outflow path 62 of each unit module 10a to 101.

[0183] The heat medium pump 21A is used to make the heat medium flow between the magnetic refrigeration module 10 and each heat exchanger 60, 70. The heat medium pump 21A is, for example, disposed on the heat medium pipeline between the low-pressure side multi-way reversing valve 120 in the rotary valve type multi-way reversing valve 100 and the second heat exchanger 17.

[0184] In the present modification, a heat medium transport unit is constituted by a heat medium pump 21A and a rotary valve type multi-way switching valve 100 .

[0185] <Operation of magnetic refrigeration device>

[0186] exist Fig.21 In the magnetic refrigeration system 1 shown, each check valve 91, 92 and the rotary valve type multi-way reversing valve 100 are controlled, and a magnetic field is applied to or removed from the storage portion 11 of the magnetic refrigeration module 10 (unit modules 10a~10l) corresponding to the control action, thereby supplying cold energy.

[0187] The following, such as Fig.21 and Fig. 22 As shown, the specific description is given by taking the case where the unit modules 20a, 20b, 20c, 20g, 20h, and 20i are excited and the unit modules 20d, 20e, 20f, 20j, 20k, and 20l are demagnetized as an example. Fig.21 In FIG. 1 , the flow of the heat medium is shown by arrows.

[0188] First, the heat medium flowing out of the second outflow portion 17a of the second heat exchanger 17 selectively flows into the low-temperature side inflow path 61 of the excited unit modules 10a, 10b, 10c, 10g, 10h, 10i under the control of the first check valve 91. The heat medium is heated by heat exchange with the magnetic working medium 12 in the heat release state in the unit modules 10a, 10b, 10c, 10g, 10h, 10i, and then flows out from the high-temperature side outflow path 64.

[0189] The heat medium flowing out of the high-temperature side outflow passage 64 of the unit modules 10a, 10b, 10c, 10g, 10h, and 10i flows into the first inflow portion 16b of the first heat exchanger 16 through the heat medium pump 21A under the control of the low-pressure side multi-way reversing valve 120. The heat medium exchanges heat with the secondary refrigerant flowing in a heat source unit (not shown) such as a cooling tower, and flows out from the first outflow portion 16a of the first heat exchanger 16.

[0190] The heat medium flowing out of the first outflow portion 16a of the first heat exchanger 16 selectively flows into the high-temperature side inflow path 63 of the demagnetized unit modules 10d, 10e, 10f, 10j, 10k, and 10l under the control of the high-pressure side multi-way reversing valve 110. The heat medium exchanges heat with the magnetic working medium 12 in the heat absorbing state in the unit modules 10d, 10e, 10f, 10j, 10k, and 10l to be cooled, and then flows out from the low-temperature side outflow path 62.

[0191] The heat medium flowing out of the low temperature side outflow passage 62 of the unit modules 10d, 10e, 10f, 10j, 10k, and 10l flows into the second inflow portion 17b of the second heat exchanger 17 under the control of the second check valve 92. The heat medium exchanges heat with the secondary refrigerant flowing in a utilization unit (not shown) such as an air handling unit, and flows out from the second outflow portion 17a of the second heat exchanger 17.

[0192] <Features of Modification 3>

[0193] In the heating operation of this variant, the flow control of the heat medium described above is repeatedly performed while selectively changing the unit module 10a that is excited or demagnetized by the magnetic field modulation unit 15. During the heating operation, if the condition for frost on the surface of the low-temperature side heat exchanger (the second heat exchanger 17) is met, the defrosting operation is performed. In the defrosting operation, for example, by electrically controlling the magnetic field modulation unit 15 and the rotary valve type multi-way reversing valve 100, the conveying direction of the heat medium in the internal flow path 13 relative to the phase of the magnetic field change is switched to a direction opposite to that of the heating operation. In this way, the enlargement of the high-temperature side heat exchanger or the complication of the device structure due to the addition of valves or tanks can be avoided, and the low-temperature side heat exchanger can be defrosted at a low cost.

[0194] (Variant 4)

[0195] In the magnetic refrigeration device 1 of the embodiment and variations 1 to 3, the following situation is described: in a structure in which the magnetic field modulation unit 15 and the heat medium transport unit, i.e., the reciprocating pump 21, and various valves are driven independently and electrically synchronized with each other, the heat medium transport direction in the internal flow path 13 relative to the phase of the magnetic field change is electrically switched.

[0196] In contrast, in the present variation, in a structure in which a phase adjustment mechanism such as an axis, a belt, or a gear is used, the magnetic field modulation unit 15 and the heat medium transport unit, i.e., a reciprocating pump 21, and various valves are driven in conjunction with each other, the magnetic field modulation unit 15 and the heat medium transport unit are mechanically controlled to switch the heat medium transport direction in the internal flow path 13 relative to the phase of the magnetic field change.

[0197] <Structure of magnetic refrigeration device>

[0198] Fig.24 FIG. 1 is a schematic diagram of the main structure of the magnetic refrigeration device 1 of this modified example. Fig.24 In Figure 21 to Figure 23 The same components of the magnetic refrigeration device 1 according to the third modification are denoted by the same reference numerals.

[0199] like Fig.24 As shown, in the magnetic refrigeration device of this variant, the rotating magnetic circuit (magnetic field modulation unit 15) and the rotary valve type multi-way reversing valve 100 in the magnetic refrigeration device 1 of the variant 3 are connected by a connecting shaft 71, thereby achieving timing (synchronization) between the magnetic field change and the flow of the heat medium.

[0200] exist Figure 24 to Figure 26In the rotary valve type multi-way reversing valve 100 shown in FIG. 1 , the high-pressure side multi-way reversing valve 110 and the low-pressure side multi-way reversing valve 120 are integrally arranged in the same valve box 101. Fig.24 In FIG. 1 , the flow of the heat medium is shown by arrows.

[0201] The rotary valve type multi-way reversing valve 100 mainly includes a valve box 101, a rotating shaft 102, a high-pressure side inlet valve port 115, a low-pressure side outlet valve port 125, a high-pressure side valve disc 111, a high-pressure side valve body 112, a low-pressure side valve disc 121, and a low-pressure side valve body 122. The valve box 101 is made of, for example, acrylic resin. The rotating shaft 102 is made of, for example, stainless steel. The high-pressure side valve disc 111 and the low-pressure side valve disc 121 are made of, for example, aluminum. The high-pressure side valve body 112 and the low-pressure side valve body 122 are made of, for example, fluororesin such as PTFE.

[0202] It should be noted that, in this modification, "axial direction" refers to the direction in which the rotation axis 102 (axial centerline J) extends, "radial direction" refers to the direction orthogonal to the rotation axis 102, and "circumferential direction" refers to the circumferential direction of a circle centered on the rotation axis 102. This is also true in the modification 5 described later.

[0203] At one axial end of the valve box 101 ( Fig.24 A high pressure side valve plate 111 is arranged at the upper end of the valve box 101. Fig.24 A low-pressure side valve disc 121 is arranged at the lower end of the valve box 101. A high-pressure side valve disc 112 is arranged on the inner side of the high-pressure side valve disc 111 in the valve box 101. A low-pressure side valve disc 122 is arranged on the inner side of the low-pressure side valve disc 121 in the valve box 101.

[0204] The rotating shaft 102 extends from the outside of the valve box 101 to the inside in a manner that penetrates the center of the high-pressure side valve disc 111. The rotating shaft 102 is rotated by a driving rotating mechanism outside the figure. A sealing component 103 such as a mechanical seal is provided between the rotating shaft 102 and the high-pressure side valve disc 111. Inside the valve box 101, a high-pressure side valve body 112 and a low-pressure side valve body 122 are mounted on the rotating shaft 102. The high-pressure side valve body 112 and the low-pressure side valve body 122 can rotate together with the rotating shaft 102.

[0205] The high-pressure valve body 112 and the low-pressure valve body 122 are driven to rotate by the same rotating shaft 102. Therefore, the high-pressure valve body 112 and the low-pressure valve body 122 rotate in the same direction at the same speed. The relative position relationship between the high-pressure valve body 112 and the low-pressure valve body 122 does not change due to the rotation.

[0206] The high-pressure inlet port 115 is located at the radial side of the valve box 101 . Thus, the interior of the valve box 101 is kept at a high pressure by communicating with the high-pressure inlet port 115 . The low-pressure outlet port 125 is provided at the center of the low-pressure valve plate 121 .

[0207] A plurality of high-pressure side outlet valve ports 113 are formed on the high-pressure side valve plate 111 in a manner of surrounding the rotating shaft 102. A high-pressure side flow path 114 is formed on the high-pressure side valve body 112. The high-pressure side flow path 114 has a structure open to the inside of the valve box 101. The high-pressure side flow path 114 is connected to at least one valve port 113a among the plurality of high-pressure side outlet valve ports 113 according to the rotation position of the high-pressure side valve body 112, so that the valve port 113a and the high-pressure side inlet valve port 115 are selectively connected. The high-pressure side valve body 112 blocks at least one valve port 113b among the plurality of high-pressure side outlet valve ports 113, which has a lower pressure than the inside of the valve box 101, according to the rotation position. Due to the pressure difference between the valve port 113b and the inside of the valve box 101, the high-pressure side valve body 112 is attracted to the side of the high-pressure side valve plate 111 and is closely attached to the high-pressure side valve plate 111, thereby preventing leakage of the fluid.

[0208] The high-pressure side valve body 112 is fixed in the circumferential direction of the rotating shaft 102, but is not fixed in the axial direction of the rotating shaft 102. For example, the cross-sectional shape of the rotating shaft 102 perpendicular to the axial direction may be set to a D shape, and a through hole of the same D shape may be set on the high-pressure side valve body 112, so that the rotating shaft 102 passes through the through hole, thereby fixing the high-pressure side valve body 112 in the circumferential direction of the rotating shaft 102 and enabling the high-pressure side valve body 112 to move in the axial direction of the rotating shaft 102. In this way, when the high-pressure side valve body 112 is attracted to the side of the high-pressure side valve plate 111, the rotating shaft 102 can be prevented from being attracted together.

[0209] A plurality of low-pressure side inlet valve ports 123 are formed on the low-pressure side valve plate 121 in a manner of surrounding the low-pressure side outlet valve port 125. A low-pressure side flow path 124 is formed on the low-pressure side valve body 122. The low-pressure side valve body 122 blocks at least one valve port 123a at high pressure among the plurality of low-pressure side inlet valve ports 123 according to the rotational position. The low-pressure side flow path 124 is connected to at least one valve port 123b having a lower pressure than the pressure inside the valve box 101 according to the rotational position of the low-pressure side valve body 122, so that the valve port 123b is selectively connected to the low-pressure side outlet valve port 125. The low-pressure side flow path 124 has a closed structure relative to the inside of the valve box 101. In other words, the high pressure inside the valve box 101 is separated from the low pressure of the low-pressure side flow path 124 (the inside of the low-pressure side valve body 122). Thus, due to the pressure difference between the interior of the low-pressure side valve body 122 and the interior of the valve box 101, the low-pressure side valve body 122 is attracted to the low-pressure side valve plate 121 and closely adheres to the low-pressure side valve plate 121, thereby preventing leakage of the fluid.

[0210] The low-pressure side valve body 122 is fixed in the circumferential direction of the rotating shaft 102, but not in the axial direction of the rotating shaft 102. For example, the cross-sectional shape of the rotating shaft 102 perpendicular to the axial direction may be set to a D shape, and a through hole of the same D shape may be provided on the low-pressure side valve body 122, so that the rotating shaft 102 passes through the through hole, thereby fixing the low-pressure side valve body 122 in the circumferential direction of the rotating shaft 102 and enabling the low-pressure side valve body 122 to move in the axial direction of the rotating shaft 102. In this way, when the low-pressure side valve body 122 is attracted to the side of the low-pressure side valve plate 121, the rotating shaft 102 is prevented from being attracted together.

[0211] As described above, the high-pressure side valve body 112 and the low-pressure side valve body 122 are constructed as different components and can move independently in the axial direction (can slide relative to the rotating shaft 102), so the attractive forces acting on the high-pressure side valve body 112 and the low-pressure side valve body 122 will not cancel each other. Since each valve body 112, 122 can move in the axial direction, when the spring 104 is set between each valve body 112, 122, the elastic force of the spring 104 can be used to make each valve body 112, 122 close to each valve plate 111, 121.

[0212] The low-pressure side valve body 122 may also include a mechanism for thermally insulating the interior of the valve box 101 from the low-pressure side flow path 124. As an example, at least a portion of the low-pressure side valve body 122 may be made of a thermal insulation material. As the thermal insulation material, a resin with low friction and excellent sliding properties, such as PTFE, POM, or the like, may also be used.

[0213] It should be noted that in Fig.21 In the heat medium circuit C shown, the high-pressure side outlet valve port 113 of the high-pressure side multi-way reversing valve 110 is connected to the high-temperature side inflow path 63 of the magnetic refrigeration module 10 (unit modules 10a~10l). The low-pressure side inlet valve port 123 of the low-pressure side multi-way reversing valve 120 is connected to the high-temperature side outflow path 64 of the magnetic refrigeration module 10. Here, the high-pressure side outlet valve port 113 and the low-pressure side inlet valve port 123 connected to the same unit module 10a~10l will not be in the "open" state at the same time. Specifically, for the high-pressure side outlet valve port 113 and the low-pressure side inlet valve port 123 connected to the same unit module 10a~10l, when one valve port is in the "open" state, the other valve port is in the "closed" state, and when one valve port is in the "closed" state, the other valve port is in the "open" or "closed" state.

[0214] However, when the internal pressure of the valve box 101 is low right after the magnetic refrigeration device 1 starts to work, or when the valve bodies 112 and 122 are pressed against the valve plates 111 and 121 in a direction opposite to the direction of gravity so that they are tightly attached, there is a possibility of insufficient adhesion and fluid leakage.

[0215] Therefore, the spring 104 is arranged inside the valve box 101 as an auxiliary device to increase the close contact between the valve bodies 112, 122 and the valve plates 111, 121. It should be noted that when the magnetic refrigeration device 1 is in normal operation, the close contact is generated by the high pressure inside the valve box 101, so the elastic force of the spring 104 only needs to be enough to make the valve bodies 112, 122 and the valve plates 111, 121 weakly close together. In this way, the wear of the valve bodies 112, 122 caused by the elastic force of the spring 104 can be suppressed.

[0216] Specifically, the spring 104 is arranged between the high-pressure side valve body 112 and the low-pressure side valve body 122. The spring 104 surrounds the outer periphery of the rotating shaft 102 and extends in the axial direction. One end of the spring 104 is mounted on the high-pressure side valve body 112, and the other end of the spring 104 is mounted on the low-pressure side valve body 122. Under this structure, other components such as a spring pressure plate are not provided. By providing the spring 104, the high-pressure side valve body 112 can be pushed onto the high-pressure side valve plate 111, and the low-pressure side valve body 122 can be pushed onto the low-pressure side valve plate 121. Since the spring 104 rotates integrally with the high-pressure side valve body 112 and the low-pressure side valve body 122, there is no need to provide sliding parts between the spring 104 and the valve bodies 112 and 122, between the spring 104 and the valve box 101, etc., so the occurrence of friction torque and wear can be avoided.

[0217] <Features of Modification 4>

[0218] In the magnetic refrigeration device 1 of this modified example, the axis (rotation mechanism 15c) of the magnetic field modulation unit 15 and the rotation axis 102 of the rotary valve type multi-way reversing valve 100 are connected by a connecting shaft 71, whereby the magnetic field modulation unit 15 and the rotary valve body (high-pressure side valve body 112, low-pressure side valve body 122) rotate through the same axis (hereinafter referred to as the common axis). On the other hand, the magnetic refrigeration module 10 is fixed.

[0219] Generally, the main body (valve box 101, valve disc (high-pressure side valve disc 111, low-pressure side valve disc 121)) of the rotary valve type multi-way reversing valve 100 is fixed, but in this modified example, the main body of the rotary valve type multi-way reversing valve 100 is rotated around a common axis. As a result, the valve port positions of the valve discs (high-pressure side valve disc 111, low-pressure side valve disc 121) move in the rotation direction, so that the timing of the flow of the heat medium can be changed (that is, the phase is staggered).

[0220] It should be noted that the rotary valve type multi-way reversing valve 100 is connected to the magnetic refrigeration module 10, the heat medium pump 21A, etc. through a pipeline. By using a flexible pipeline (resin pipe, etc.), the main body of the rotary valve type multi-way reversing valve 100 can be easily rotated. In the case of using a two-pole magnet 15a, the rotation angle for phase adjustment is usually within ±90°, so the maximum rotation angle of the main body of the rotary valve type multi-way reversing valve 100 in the defrosting operation is also about 90°.

[0221] The main body of the rotary valve type multi-way selector valve 100 can be rotated by using, for example, a stepping motor or a servo motor, thereby enabling arbitrary angle control.

[0222] According to the above-described configuration, phase adjustment (switching the heat medium conveying direction in the internal flow path 13 relative to the phase of magnetic field fluctuation) can be performed even during the rotation of the magnetic field modulator 15 and the rotary valve type multi-way switching valve 100 .

[0223] (Variant 5)

[0224] The difference between the magnetic refrigeration device 1 of this modification and the modification 4 is that a magnetic field modulator 15 is provided between the rotary magnetic circuit (magnetic field modulator 15) and the rotary valve type multi-way switching valve 100. Fig. 27 or Fig.28 Phase adjustment mechanisms 200, 300 are shown.

[0225] Fig. 27 The phase adjustment mechanism 200 shown has four bevel gears 206a, 206b, 206c, 206d (collectively referred to as bevel gear set 206) and two spur gears 208a, 208b (collectively referred to as spur gear set 208) in a housing 201. The bevel gear set 206 is housed in the upper housing 202, and the spur gear set 208 is housed in the lower housing 203. The input shaft 204 is arranged to be supported by the bevel gear set 206 (bevel gear 206a) at one end and to pass through the top of the upper housing 202. The output shaft 205 is arranged to be supported by the spur gear set 208 (spur gear 208b) at one end and to pass through the bottom of the lower housing 203. The connecting shaft 207 is provided with one end supported by the bevel gear set 206 (bevel gear 206b) and the other end supported by the spur gear set 208 (spur gear 208a), and passes through the bottom of the upper housing 202 (the top of the lower housing 203).

[0226] It should be noted that Fig. 27 The figure above shows the cross-sectional structure of the phase adjustment mechanism 200 when viewed from the axial direction. Fig. 27 The figure below shows the cross-sectional structure of the phase adjustment mechanism 200 when viewed from the radial direction.

[0227] The bevel gear set 206 performs phase adjustment (switches the heat medium conveying direction in the internal flow path 13 relative to the phase of the magnetic field change). The spur gear set 208 changes the rotation direction of the output shaft 205 coaxial with the rotating shaft 102 of the rotary valve type multi-way reversing valve 100 to the same direction as the input shaft 204, wherein the input shaft 204 is coaxial with the shaft (rotating mechanism 15c) of the magnetic field modulation unit 15. The two bevel gears 206c and 206d in the bevel gear set 206 are arranged to be rotatable relative to the input shaft 204. By rotating the two bevel gears 206c and 206d, the phase difference (hereinafter referred to as the phase rotation angle) between the input shaft 204 and the output shaft 205 can be changed. The shafts 211 and 213 of the bevel gears 206c and 206d are supported by bearings 212 and 214 provided on the support member 210 in the upper housing 202, respectively. If the rotation angle of the bevel gears 206c and 206d (hereinafter referred to as the phase adjustment angle) is changed, the output shaft 205 will have a phase rotation angle twice the phase adjustment angle in the direction opposite to the rotation direction of the bevel gears 306c and 306d. In the control of the phase adjustment angle, for example, a stepping motor or a servo motor is used, thereby enabling arbitrary angle control. According to the structure described above, phase adjustment (switching the heat medium transport direction in the internal flow path 13 relative to the phase of the magnetic field change) can be performed even during the rotation of the magnetic field modulation unit 15 and the rotary valve type multi-way reversing valve 100. Since the main body of the rotary valve type multi-way reversing valve 100 can be kept fixed, there will be no restrictions on pipelines, etc.

[0228] It should be noted that you can also Fig. 27 The spur gear set 208 of the phase adjustment mechanism 200 shown in the figure is replaced with a bevel gear, thereby forming Fig.28 The phase adjustment mechanism 300 shown. It should be noted that, Fig.28 The cross-sectional structure of the phase adjustment mechanism 300 as viewed from the radial direction is shown.

[0229] The phase adjustment mechanism 300 has a first bevel gear set 306 composed of four bevel gears 306a, 306b, 306c, and 306d and a second bevel gear set 307 composed of four bevel gears 307a, 307b, 307c, and 307d in a housing 301. The first bevel gear set 306 is accommodated in an upper space 302 of the housing 301, and the second bevel gear set 307 is accommodated in a lower space 303 of the housing 301. The input shaft 304 is arranged to be supported at one end by the first bevel gear set 306 (bevel gear 306a) and to pass through the top of the housing 301. The output shaft 305 is arranged to be supported at one end by the second bevel gear set 307 (bevel gear 307b) and to pass through the bottom of the housing 301. It should be noted that the bevel gear set 306 b opposite to the bevel gear 306 a in the first bevel gear set 306 and the bevel gear 307 a opposite to the bevel gear 307 b in the second bevel gear set 307 are integrally formed.

[0230] The first bevel gear set 306 performs phase adjustment (switching the heat medium conveying direction in the internal flow path 13 relative to the phase of the magnetic field change). The second bevel gear set 307 changes the rotation direction of the output shaft 305 coaxial with the rotating shaft 102 of the rotary valve type multi-way reversing valve 100 to the same direction as the input shaft 304, wherein the input shaft 304 is coaxial with the axis of the magnetic field modulation unit 15 (rotating mechanism 15c).

[0231] The two bevel gears 306c and 306d in the first bevel gear set 306 are arranged to be rotatable relative to the input shaft 304. By rotating the two bevel gears 306c and 306d, the phase difference (hereinafter referred to as the phase rotation angle) between the input shaft 304 and the output shaft 305 can be changed. The shafts 311 and 313 of the bevel gears 306c and 306d are supported by bearings 312 and 314 provided on the supporting member in the upper space 302, respectively. If the rotation angle (hereinafter referred to as the phase adjustment angle) of the bevel gears 306c and 306c is changed, the output shaft 305 will have a phase rotation angle twice the size of the phase adjustment angle in the direction opposite to the rotation direction of the bevel gears 306c and 306d. In the control of the phase adjustment angle, for example, a stepping motor or a servo motor is used, thereby enabling arbitrary angle control.

[0232] The two bevel gears 307c and 307d in the second bevel gear set 307 are rotatably provided relative to the output shaft 305. The shafts 321 and 323 of the bevel gears 307c and 307d are supported by bearings 322 and 324 provided on the side wall portion of the housing 301, respectively.

[0233] According to the structure described above, phase adjustment (switching the heat medium conveying direction in the internal flow path 13 relative to the phase of the magnetic field change) can be performed even during the rotation of the magnetic field modulation unit 15 and the rotary valve type multi-way reversing valve 100. Since the main body of the rotary valve type multi-way reversing valve 100 can be kept fixed, there is no restriction on the pipeline, etc. Furthermore, since the input shaft 304 and the output shaft 305 can be arranged on the same axis, the phase adjustment mechanism 300 can be easily set between the rotary magnetic circuit (magnetic field modulation unit 15) and the rotary valve type multi-way reversing valve 100.

[0234] (Variant 6)

[0235] Fig.29 FIG. 1 is a piping system diagram of the magnetic refrigeration device 1 according to the sixth modification. Fig.29 In Figure 1 The same components as those in the above-described embodiments are denoted by the same reference numerals.

[0236] In the magnetic refrigeration device 1 of this modification example 6, Fig.29 As shown, a first fan 16f is arranged near the first heat exchanger 16. The first fan 16f is driven by a first motor 16m. A second fan 17f is arranged near the second heat exchanger 17. The second fan 17f is driven by a second motor 17m. The first motor 16m and the second motor 17m are controlled and driven by the control unit 30.

[0237] The present modification is characterized in that, during the defrosting operation of the above-described embodiment, operation control of the fans 16f and 17f is performed as follows.

[0238] In the first fan control, the second fan 17f is stopped during the defrosting operation when the temperature of the second heat exchanger 17 is higher than the ambient temperature of the second heat exchanger 17. In this way, when the second heat exchanger 17 is a low-temperature side heat exchanger (for example, an outdoor heat exchanger) and the temperature of the outdoor heat exchanger is higher than the outdoor air temperature, the second fan 17f is stopped, thereby preventing heat from being released from the outdoor heat exchanger to the outside air, thereby enabling efficient defrosting.

[0239] Alternatively, the second fan control described below may be performed instead of the first fan control, or the second fan control described below may be performed in addition to the first fan control.

[0240] In the second fan control, the first heat exchanger 16 is an indoor heat exchanger, and the first fan (indoor fan) 16f is stopped during the defrosting operation. This can suppress the temperature drop of the indoor space caused by the cold air sent from the indoor unit provided with the indoor heat exchanger.

[0241] (Other embodiments)

[0242] In the above-described embodiments and variations, a magnetic refrigeration device is exemplified as a solid-state refrigeration device, but the solid-state refrigeration device may also be a device using other methods other than magnetic refrigeration to induce magnetocaloric effect in the magnetic working medium 12. It should be noted that in the present disclosure, solid refrigerant substances also include substances having intermediate properties between liquid and solid, such as plastic crystals.

[0243] Other types of solid-state refrigeration devices include: 1) a method of inducing an electrocaloric effect in a solid refrigerant substance, 2) a method of inducing a pressure-caloric effect in a solid refrigerant substance, and 3) a method of inducing an elastic-caloric effect in a solid refrigerant substance.

[0244] In the solid-state refrigeration device of method 1), the force field applying unit (hereinafter also referred to as the inducing unit) applies electric field fluctuations to the solid refrigerant substance. As a result, the solid refrigerant substance undergoes a phase change from a ferroelectric to a paraelectric, and the solid refrigerant substance generates or absorbs heat.

[0245] In the solid-state refrigeration device of aspect 2), by applying pressure fluctuation to the solid refrigerant substance by the inducing unit, the solid refrigerant substance undergoes a phase change and generates or absorbs heat.

[0246] In the solid-state refrigeration device of aspect 3), stress variation is applied to the solid refrigerant substance by the inducing portion, whereby the solid refrigerant substance undergoes a phase change and generates or absorbs heat.

[0247] The above embodiments and variations are described, but it should be understood that various changes can be made to the methods and details without departing from the subject matter and scope of the claims. The above embodiments and variations can also be appropriately combined or replaced. The terms "first", "second", etc. mentioned above are only used to distinguish the sentences containing the terms, and are not intended to limit the number or order of the sentences.

[0248] - Industrial Applicability -

[0249] In summary, the present disclosure is useful for solid-state refrigeration devices, especially for magnetic refrigeration devices.

[0250] - Explanation of symbols -

[0251] 1Magnetic Refrigeration Device (Solid State Refrigeration Device)

[0252] 11 Storage Department

[0253] 11a~11e Partial storage area

[0254] 12 Magnetic medium (solid refrigerant material)

[0255] 12a~12e Various substances with different temperatures for maximum thermal effect

[0256] 13Internal flow path

[0257] 15 Magnetic field modulation unit (force field modulation unit)

[0258] 16First heat exchanger

[0259] 16f first fan (indoor fan)

[0260] 17 Second heat exchanger

[0261] 17f Second fan (fan)

[0262] 21 Reciprocating pump (heat medium transport unit)

[0263] 50Heat medium transport unit

[0264] 100 Rotary valve type multi-way reversing valve (heat medium transport part)

[0265] C Heat medium circuit

Claims

1. A solid-state refrigeration device, comprising a storage unit (11), a force field modulation unit (15), a first heat exchanger (16), a second heat exchanger (17), a heat medium circuit (C), and a heat medium transport unit (21, 50, 100), The storage portion (11) has a solid refrigerant substance (12) and an internal flow path (13), and a heat medium flows in the internal flow path (13) and performs heat exchange with the solid refrigerant substance (12). The force field modulation unit (15) imparts force field changes to the solid refrigerant material (12) in the storage unit (11) to induce a thermal effect. The first heat exchanger (16), the second heat exchanger (17) and the internal flow path (13) are connected in the heat medium circuit (C). The heat medium transport unit (21, 50, 100) transports the heat medium back and forth to the solid refrigerant substance (12) in the storage unit (11) in accordance with the force field change in the heat medium circuit (C). The solid-state refrigeration device (1) performs a heating operation and a defrosting operation. In the heating operation, the heat medium heated by the solid refrigerant substance (12) releases heat in the first heat exchanger (16) and the heat medium cooled by the solid refrigerant substance (12) absorbs heat in the second heat exchanger (17). In the defrosting operation, frost attached to the second heat exchanger (17) during the heating operation is removed. The invention is characterized in that: The solid refrigerant substance (12) includes a plurality of substances (12a-12e) having different temperatures with the greatest thermal effects. The plurality of substances (12a-12e) are arranged along the internal flow path (13) in the order of high and low temperatures. In the defrosting operation, the conveying direction of the heat medium in the internal flow path (13) is switched to a direction opposite to that in the heating operation with respect to a phase of the force field variation.

2. The solid-state refrigeration device according to claim 1, characterized in that: The storage unit (11) includes a plurality of partial storage units (11a to 11e) connected in series with each other in the heat medium circuit (C). The plurality of partial storage sections (11a to 11e) respectively contain at least one substance among the plurality of substances (12a to 12e).

3. The solid-state refrigeration device according to claim 1 or 2, characterized in that: The force field modulation unit (15) and the heat medium transport unit (21, 50, 100) are electrically controlled to switch the transport direction of the heat medium in the internal flow path (13) relative to the phase of the force field variation.

4. The solid-state refrigeration device according to claim 1 or 2, characterized in that: The force field modulation unit (15) and the heat medium transport unit (100) are mechanically controlled to switch the transport direction of the heat medium in the internal flow path (13) relative to the phase of the force field variation.

5. The solid-state refrigeration device according to any one of claims 1 to 4, characterized in that: The solid-state refrigeration device further comprises a fan (17f) for supplying air to the second heat exchanger (17). When the temperature of the second heat exchanger (17) is higher than the ambient temperature of the second heat exchanger (17), the fan (17f) is stopped during the defrosting operation.

6. The solid-state refrigeration device according to any one of claims 1 to 5, characterized in that: The first heat exchanger (16) is an indoor heat exchanger, The solid-state refrigeration device further comprises an indoor fan (16f) for supplying air to the indoor heat exchanger. During the defrosting operation, the indoor fan (16f) is stopped.

7. The solid-state refrigeration device according to any one of claims 1 to 6, characterized in that: The frequency of the force field variation is increased during the defrosting operation.

8. The solid-state refrigeration device according to any one of claims 1 to 7, characterized in that: During the defrosting operation, the flow rate of the heat medium in the heat medium circuit (C) is increased.

9. The solid-state refrigeration device according to any one of claims 1 to 8, characterized in that: The solid refrigerant substance (12) is a magnetic refrigerant (12), The force field modulation unit (15) is a magnetic field modulation unit (15) that imparts magnetic field fluctuations to the magnetic medium (12).

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