Solid freezing equipment

Abstract

To defrost a low-temperature side heat exchanger while avoiding increase in size and complication of a solid freezer.SOLUTION: A solid freezer (1) performs heating operation and defrosting operation. In the defrosting operation, frost adhering to a second heat exchanger (17) is removed during the heating operation. A solid refrigerant substance (12) includes a plurality of substances (12a to 12e) having different temperatures at which a calorific effect is maximum. The plurality of substances (12a to 12e) are arranged along an internal flow path (13) in descending order of temperature. In the defrosting operation, a conveyance direction of a heat medium in the internal flow path (13) with respect to a phase of force field fluctuation is switched to an opposite direction to that in the heating operation.SELECTED DRAWING: Figure 5

Description

[Technical Field]

[0001] The present disclosure relates to solid-state refrigeration devices. [Background technology]

[0002] The magnetic refrigeration apparatus disclosed in Patent Document 1 has multiple beds, a high-temperature heat exchanger, and a low-temperature heat exchanger. The beds, the high-temperature heat exchanger, and the low-temperature heat exchanger are connected to a heat transfer medium circuit. In the beds, the magnetic working material generates or absorbs heat as the magnetic field of the magnetic working material fluctuates. The heat transfer medium in the heat transfer medium circuit is heated by the magnetic working material that generates heat, or cooled by the magnetic working material that absorbs heat. This operation generates a temperature difference between the heat transfer medium in the high-temperature heat exchanger and the heat transfer medium in the low-temperature heat exchanger.

[0003] Since the temperature of the heat medium in the low-temperature side heat exchanger is low, frost may form on the surface of the low-temperature side heat exchanger. In Patent Document 1, the heat medium stored in the high-temperature side heat exchanger is transported to the low-temperature side heat exchanger to defrost the low-temperature side heat exchanger. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Laid-Open No. 2016-11799 Summary of the Invention [Problem to be solved by the invention]

[0005] However, according to the defrosting method of Patent Document 1, the heat medium stored in the high-temperature side heat exchanger is used to defrost the low-temperature side heat exchanger, so in order to ensure sufficient heat to melt the frost, the size of the high-temperature side heat exchanger must be larger than that of the low-temperature side heat exchanger. Also proposed is a method of switching the high-temperature side and the low-temperature side by flow path switching and defrosting with the heat generated by the magnetic working material, but this method requires adding a valve to the heat medium circuit. Also proposed is a method of storing heat from the high-temperature side and switching the flow path during defrosting to defrost with the stored heat, but this method requires adding a valve and a tank to the heat medium circuit.

[0006] An object of the present disclosure is to enable defrosting of a low-temperature side heat exchanger while avoiding an increase in size and complexity of a solid-state refrigeration device such as a magnetic refrigeration device. [Means for solving the problem]

[0007] A first aspect of the present disclosure is a solid-state refrigeration device (1) including 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 unit (11) has a solid refrigerant material (12) and an internal flow path (13) through which a heat medium flows and exchanges heat with the solid refrigerant material (12). The force field modulation unit (15) applies a force field fluctuation to the solid refrigerant material (12) in the storage unit (11) to induce a calorific 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 unit (21, 50, 100) transports the heat medium back and forth to the solid refrigerant material (12) in the storage unit (11) in the heat medium circuit (C) in response to the force field fluctuation. The solid refrigeration device (1) performs a heating operation and a defrosting operation. In the heating operation, the heat medium heated by the solid refrigerant material (12) is released in the first heat exchanger (16), and the heat medium cooled by the solid refrigerant material (12) is absorbed in the second heat exchanger (17). In the defrosting operation, frost formed on the second heat exchanger (17) during the heating operation is removed. The solid refrigerant material (12) includes a plurality of substances (12a to 12e) having different temperatures at which the calorific effect is maximized, and the plurality of substances (12a to 12e) are arranged along the internal flow path (13) in order of decreasing temperature. In the defrosting operation, the transport direction of the heat medium in the internal flow path (13) relative to the phase of the force field fluctuation is switched to the opposite direction to that in the heating operation.

[0008] In the first mode, in the defrosting operation, the transport direction of the heat medium in the internal flow path (13) relative to the phase of the force field fluctuation is switched to the opposite direction from that in the heating operation, thereby making it possible to defrost the low-temperature side heat exchanger without increasing the size of the high-temperature side heat exchanger or complicating the device structure by adding a valve, a tank, or the like.

[0009] A second aspect of the present disclosure is the first aspect, wherein the storage section (11) includes a plurality of partial storage sections (11a to 11e) connected in series to each other in the heat medium circuit (C), and each of the plurality of partial storage sections (11a to 11e) has at least one substance among the plurality of substances (12a to 12e).

[0010] In the second embodiment, the degree of freedom in cascade configuration of the solid refrigerant material (12) is increased.

[0011] A third aspect of the present disclosure is the first or second aspect, in which 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) according to the phase of the force field fluctuation.

[0012] In the third aspect, defrosting can be performed by electrical control while avoiding an increase in size and complexity of the device.

[0013] A fourth aspect of the present disclosure is the first or second aspect, in which 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) according to the phase of the force field fluctuation.

[0014] In the fourth aspect, it is possible to defrost the low-temperature side heat exchanger by mechanical control while avoiding an increase in size and complexity of the device.

[0015] A fifth aspect of the present disclosure is any one of the first to fourth aspects, further comprising a fan (17f) that sends 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 defrosting operation.

[0016] In the fifth aspect, 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 fan (17f) is stopped to prevent heat from being dissipated from the outdoor heat exchanger to the outdoor air, thereby enabling efficient defrosting.

[0017] A sixth aspect of the present disclosure is any one of the first to fifth aspects, wherein the first heat exchanger (16) is an indoor heat exchanger, and further includes an indoor fan (16f) that blows air to the indoor heat exchanger, and the indoor fan (16f) is stopped during the defrosting operation.

[0018] In the sixth aspect, by stopping the indoor fan (16f) during defrosting, it is possible to prevent the temperature of the indoor space from decreasing due to the blowing of cold air from the indoor unit provided with the indoor heat exchanger.

[0019] A seventh aspect of the present disclosure is any one of the first to sixth aspects, wherein the frequency of the force field fluctuation is increased during the defrosting operation.

[0020] In the seventh aspect, the flow rate of the heat medium increases, which increases the pressure loss, and as a result, the amount of heat transferred to the heat medium also increases. Furthermore, eddy current loss increases in the constituent materials of the housing portion (11) and the constituent materials (such as the yoke) of the force field modulation portion (15) adjacent to the constituent materials, which further increases the amount of heat transferred to the heat medium. Therefore, the defrosting speed can be increased.

[0021] An eighth aspect of the present disclosure is any one of the first to seventh aspects, wherein in the defrosting operation, the flow rate of the heat medium in the heat medium circuit (C) is increased.

[0022] In the eighth aspect, the flow rate of the heat medium increases, which increases the pressure loss, and as a result, the amount of heat transferred to the heat medium also increases, making it possible to speed up defrosting.

[0023] A ninth aspect of the present disclosure is any one of the first to eighth aspects, wherein the solid refrigerant material (12) is a magnetically activating material (12), and the force field modulation unit (15) is a magnetic field modulation unit (15) that applies a magnetic field fluctuation to the magnetically activating material (12).

[0024] In the ninth aspect, the magnetic refrigeration device can be started up quickly. [Brief explanation of the drawings]

[0025] [Figure 1] FIG. 1 is a piping diagram of a magnetic refrigeration device according to an embodiment. [Figure 2] FIG. 2 is a diagram showing a schematic diagram of the relationship between the temperature of a plurality of solid refrigerant materials arranged in a cascade configuration in a single container in the magnetic refrigeration device according to the embodiment and the magnetic refrigeration effect. [Figure 3] FIG. 3 is a diagram showing a schematic diagram of the relationship between the temperature of a plurality of solid refrigerant materials arranged in a cascade pattern in a plurality of partial containing sections in the magnetic refrigeration device according to the embodiment and the magnetic refrigeration effect. [Figure 4] FIG. 4 is a piping diagram for explaining the heating operation performed by the magnetic refrigeration apparatus according to the embodiment. [Figure 5] FIG. 5 is a piping diagram for explaining the defrosting operation performed by the magnetic refrigeration apparatus according to the embodiment. [Figure 6] FIG. 6 is a diagram showing the relationship between magnetic field fluctuation and the heat medium transfer direction during the heating operation performed by the magnetic refrigeration device according to this embodiment. [Figure 7] FIG. 7 is a diagram showing the relationship between magnetic field fluctuation and the heat medium transfer direction during the defrosting operation performed by the magnetic refrigeration device according to this embodiment. [Figure 8] FIG. 8 is a piping diagram of the magnetic refrigeration apparatus according to the first modification. [Figure 9] FIG. 9 is a schematic configuration diagram of a magnetic refrigeration unit according to the first modification. [Figure 10] FIG. 10 is a schematic diagram illustrating the operation of the magnetic refrigeration unit according to the first modification. [Figure 11]FIG. 11 is a schematic diagram illustrating the operation of the magnetic refrigeration unit according to the first modification. [Figure 12] FIG. 12 is a piping diagram illustrating the cooling operation in the magnetic refrigeration apparatus according to the first modification. [Figure 13] FIG. 13 is a piping diagram illustrating the heating operation in the magnetic refrigeration apparatus according to the first modification. [Figure 14] FIG. 14 is a piping diagram illustrating the defrosting operation in the magnetic refrigeration apparatus according to the first modification. [Figure 15] FIG. 15 is a piping diagram of a magnetic refrigeration apparatus according to the second modification. [Figure 16] FIG. 16 is a schematic configuration diagram of a magnetic refrigeration unit according to the second modification. [Figure 17] FIG. 17 is a schematic diagram illustrating the operation of the magnetic refrigeration unit according to the second modification. [Figure 18] FIG. 18 is a piping diagram illustrating the cooling operation in the magnetic refrigeration apparatus according to the second modification. [Figure 19] FIG. 19 is a piping diagram illustrating the heating operation in the magnetic refrigeration apparatus according to the second modification. [Figure 20] FIG. 20 is a piping diagram illustrating the defrosting operation in the magnetic refrigeration apparatus according to the second modification. [Figure 21] FIG. 21 is a piping diagram of a magnetic refrigeration apparatus according to the third modification. [Figure 22] FIG. 22 is a plan view of the magnetic refrigeration module of the magnetic refrigeration device shown in FIG. 21, viewed from the axial direction of the annular housing portion. [Figure 23] FIG. 23 is a cross-sectional view of the magnetic refrigeration module of the magnetic refrigeration device shown in FIG. 21, viewed from the radial direction of the annular housing portion. [Figure 24] FIG. 24 is a schematic diagram of the main components 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 fourth modification. [Figure 25] FIG. 25 is a plan view of the high-pressure side valve plate of the rotary valve type multi-way switching valve shown in FIG. 24, viewed from the outside of the valve body. [Figure 26] FIG. 26 is a plan view of the low-pressure side valve plate of the rotary valve type multi-way switching valve shown in FIG. 24 as seen from outside the valve body. [Figure 27] FIG. 27 is a schematic diagram of an example of a phase adjuster mechanism that performs mechanical control of the magnetic field modulation section (15) in the magnetic refrigeration device according to the fifth modification. [Figure 28] FIG. 28 is a schematic diagram of another example of the phase adjuster mechanism for mechanically controlling the magnetic field modulation section (15) in the magnetic refrigeration device according to the fifth modification. [Figure 29] FIG. 29 is a piping diagram of a magnetic refrigeration apparatus according to the sixth modification. DETAILED DESCRIPTION OF THE INVENTION

[0026] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. Note that the following embodiments are essentially preferred examples and are not intended to limit the scope of the present invention, its applications, or its uses.

[0027] (Embodiment) An embodiment will be described. The magnetic refrigeration device (1) of this embodiment is a solid-state refrigeration device that adjusts the temperature of a heat medium by utilizing the magnetocaloric effect, and is applied to, for example, an air conditioner. In this case, the magnetic refrigeration device (1) adjusts the temperature of air in a space to be air-conditioned. The space to be air-conditioned is, for example, an indoor space. The magnetic refrigeration device (1) switches between a heating operation and a defrosting operation.

[0028] <Configuration of magnetic refrigeration device> As shown in Fig. 1, the magnetic refrigeration device (1) includes a heat medium circuit (C) filled with a heat medium. The filled heat medium is transported through the heat medium circuit (C). The heat medium includes, for example, a refrigerant, water, brine, etc.

[0029] The magnetic refrigeration device (1) mainly includes a storage unit (11), a magnetic field modulation unit (15) that is a force field modulation unit, a first heat exchanger (16), a second heat exchanger (17), a reciprocating pump (21) that is 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 one another via heat medium piping to form a heat medium circuit (C).

[0030] The storage section 11 has a magnetically active material 12, which is a solid refrigerant material, and an internal flow path 13 through which a heat transfer medium flows and exchanges heat with the solid refrigerant material 12. The storage section 11 is a hollow case or column. The storage section 11 is filled with the magnetically active material 12.

[0031] The magnetic working material (12) generates heat when a magnetic field is applied or when the applied magnetic field becomes stronger. The magnetic working material (12) absorbs heat when the magnetic field is removed or when the applied magnetic field becomes weaker. Examples of the material for the magnetic working material (12) include Gd5(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 ) etc. can be used.

[0032] As shown in FIG. 2, the magnetic working material (12) is composed of a plurality of materials (12a-12e) having different Curie temperatures at which the calorific effect (magnetic refrigeration effect) is maximized. The materials (12a-12e) are arranged along the internal flow path (13) in descending order of Curie temperature (i.e., in a cascade configuration). Specifically, in the storage section (11), five types of magnetic working materials (12), namely, a first material (12a), a second material (12b), a third material (12c), a fourth material (12d), and a fifth material (12e), are arranged in order from the high temperature side to the low temperature side. The various magnetic working materials (12) have different Curie temperatures, i.e., different relationships between temperature and magnetic refrigeration effect. In this example, if 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, the relationship Ta>Tb>Tc>Td>Te is satisfied.

[0033] In the cascade arrangement shown in FIG. 2, five types of magnetic working materials (12) are arranged in a single storage unit (11). However, the types of materials of the magnetic working materials (12) and the configuration of the cascade arrangement are not particularly limited. For example, multiple storage units (11) each having multiple types of cascaded magnetic working materials (12) may be arranged in parallel. Alternatively, as shown in FIG. 3, the storage unit (11) may be composed of multiple partial storage units (11a-11e) connected in series to each other in the heat medium circuit (C), and each of the multiple partial storage units (11a-11e) may store a corresponding one of the multiple substances (12a-12e). In this case, a single substance may be arranged in all of the partial storage units (11a-11e), or two or more substances may be arranged in a cascade arrangement. Alternatively, a single substance may be placed in one or more partial containers (11a-11e), and two or more substances may be cascaded in one or more other partial containers (11a-11e). In either container configuration, multiple substances (12a-12e) are placed in order of temperature along the internal flow path (13) of the serially connected partial containers (11a-11e).

[0034] The magnetic field modulation unit (15) applies a magnetic field fluctuation to the magnetic working material (12) in the container (11) to induce a calorific effect. The magnetic field modulation unit (15) is configured, for example, with an electromagnet capable of modulating a magnetic field. The magnetic field modulation unit (15) performs a first modulation operation and a second modulation operation. In the first modulation operation, a predetermined magnetic field is applied to the magnetic working material (12). In the second modulation operation, a magnetic field smaller than the predetermined magnetic field is applied or the predetermined magnetic field is removed.

[0035] The first heat exchanger (16) may be an indoor heat exchanger that exchanges heat between the heat medium heated by the magnetic working material (12) and indoor air. Alternatively, the first heat exchanger (16) may exchange heat between the heat medium heated by the magnetic working material (12) and a secondary refrigerant flowing through a utilization unit (not shown) (e.g., an air handling unit). The second heat exchanger (17) may be an outdoor heat exchanger that exchanges heat between the heat medium cooled by the magnetic working material (12) and outdoor air. Alternatively, the second heat exchanger (17) may exchange heat between the heat medium cooled by the magnetic working material (12) and a secondary refrigerant flowing through a heat source unit (not shown) (e.g., a cooling tower). 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 accommodation unit (11).

[0036] The reciprocating pump (21) reciprocates to transport the heat medium to the magnetic working material (12) in the container (11) in response to magnetic field fluctuations. The reciprocating pump (21) is, for example, a piston pump. The reciprocating pump (21) includes a pump case (22), a piston (23), and a drive mechanism (not shown). The piston (23) is disposed inside the pump case (22). The piston (23) divides the interior of the pump case (22) into two chambers. In the heat medium circuit (C), one chamber (hereinafter referred to as the first chamber) of the pump case (22) is connected to the first heat exchanger (16), and the other chamber (hereinafter referred to as the second chamber) of the pump case (22) is connected to the second heat exchanger (17). The drive mechanism includes a rod connected to the piston (23), a crank connected to the rod, and an electric motor that drives the crank. When the electric motor rotates the crank, the rod moves back and forth, causing the piston (23) to reciprocate within the pump case (22).

[0037] Specifically, the reciprocating pump (21) alternately performs a first transfer operation and a second transfer operation. In the first transfer operation, the piston (23) moves in a direction that expands the first chamber and contracts the second chamber. As a result, the heat medium is discharged from the second chamber, and in the heat medium circuit (C), the heat medium moves sequentially toward the second heat exchanger (17), the accommodating section (11) (internal flow path (13)), and the first heat exchanger (16), and is then drawn into the first chamber. In the second transfer operation, the piston (23) moves in a direction that contracts the first chamber and expands the second chamber. As a result, the heat medium is discharged from the first chamber, and in the heat medium circuit (C), the heat medium moves sequentially toward the first heat exchanger (16), the accommodating section (11) (internal flow path (13)), and the second heat exchanger (17), and is then drawn into the second chamber.

[0038] The control unit 30 controls the operation of, for example, the magnetic field modulation unit 15 and the reciprocating pump 21. The control unit 30 is configured using, for example, a microcomputer and a memory device (specifically, a semiconductor memory) that stores software for operating the microcomputer. The control unit 30 is connected to the magnetic field modulation unit 15 and the reciprocating pump 21 via communication lines.

[0039] <Operation of magnetic refrigeration equipment> The magnetic refrigeration device (1) performs a heat dissipation operation (hot blow) and a heat absorption operation (cold blow). In the heat dissipation operation, a predetermined magnetic field is applied to the magnetic working material (12) and a heat medium is moved in a first direction in the internal flow path (13), so that the hot heat generated in the magnetic working material (12) is transported by the heat medium to the outside of the accommodation unit (11), for example, to a first heat exchanger (16), and dissipated. In the heat absorption operation, a magnetic field weaker than the predetermined magnetic field is applied to the magnetic working material (12) or the predetermined magnetic field is removed, so that the heat medium is moved in a second direction opposite to the first direction in the internal flow path (13), so that the cold heat generated in the magnetic working material (12) is transported by the heat medium to the outside of the accommodation unit (11), for example, to a second heat exchanger (17), and absorbed.

[0040] 4(a) and 4(b), the heat dissipation operation includes a first modulation operation (excitation) of the magnetic field modulation unit (15) and a first transport operation of the reciprocating pump (21). In the heat dissipation operation, the heat medium is heated in the internal flow path (13) of the storage unit (11). The heated heat medium dissipates heat in the first heat exchanger (16).

[0041] 4(c) and 4(d), the heat absorption operation involves a second modulation operation (demagnetization) of the magnetic field modulation unit (15) and a second transport operation of the reciprocating pump (21). 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).

[0042] In the magnetic refrigeration device (1), when a cycle (AMR (Active Magnetic Refrigerator) cycle) in which the heat dissipation and heat absorption operations described above are repeated is performed, the magnetic working material (12) in the storage section (11) generates and regenerates hot and cold heat due to magnetic field fluctuations, and as a result, a temperature gradient is generated in the storage section (11), resulting in a large temperature difference between the high-temperature end and the low-temperature end of the storage section (11).

[0043] When the first heat exchanger (16) is an indoor heat exchanger and the second heat exchanger (17) is an outdoor heat exchanger, the heat medium heated by the magnetic working material (12) dissipates heat to the indoor air in the first heat exchanger (16) which is a high-temperature side heat exchanger, thereby heating the indoor air, while the heat medium cooled by the magnetic working material (12) absorbs heat from the outdoor air in the second heat exchanger (17) which is a low-temperature side heat exchanger, as shown in Fig. 4. This enables heating operation.

[0044] In the heating operation, the temperature of the heat medium in the second heat exchanger (17) decreases, and frost may form on the surface of the second heat exchanger (17). In the defrosting operation for removing the frost, in this embodiment, as shown in Fig. 5, the transport direction of the heat medium in the internal flow path (13) relative to the phase of the magnetic field fluctuation is switched to the opposite direction to that in the heating operation shown in Fig. 4.

[0045] 5(a) and 5(b), the magnetic field modulation unit (15) performs a second modulation operation (demagnetization) and the reciprocating pump (21) performs a first transfer operation, and the heat medium cooled in the internal flow path (13) of the storage unit (11) absorbs heat in the first heat exchanger (16). On the other hand, in the operation shown in Fig. 5(c) and 5(d), the magnetic field modulation unit (15) performs a first modulation operation (excitation) and the reciprocating pump (21) performs a second transfer operation, and the heat medium heated in the internal flow path (13) of the storage unit (11) dissipates heat in the second heat exchanger (17), thereby performing defrosting. As described above, in the defrosting operation of this embodiment, the timing of the magnetic field fluctuation and the heat medium flow, i.e., the AMR (Active Magnetic Refrigerator) cycle, is reversed (180° phase inversion) as shown in Fig. 7 compared to the heating operation shown in Fig. 6. In Figs. 6 and 7, (A) indicates the magnetic field fluctuation, and (B) indicates the heat medium transport direction. As a result, heat is transferred from the high-temperature side to the low-temperature side, heating the outdoor heat exchanger (second heat exchanger (17)), which is the low-temperature side heat exchanger, and defrosting is performed.

[0046] In the present embodiment, the internal flow path (13) is arranged along the longitudinal direction of the storage section (11), in other words, the high-temperature side inlet / outlet port and the low-temperature side inlet / outlet port of the internal flow path (13) are arranged at both ends of the storage section (11) in the longitudinal direction, respectively. However, the arrangement of the internal flow path (13) is not limited to this. For example, the high-temperature side inlet / outlet port and the low-temperature side inlet / outlet port of the internal flow path (13) may be arranged on the same face of the storage section (11). In this case, too, the direction in which the heat medium flows from the low-temperature side inlet / outlet port to the high-temperature side inlet / outlet port in the internal flow path (13) is the "first direction," and the direction in which the heat medium flows from the high-temperature side inlet / outlet port to the low-temperature side inlet / outlet port is the "second direction."

[0047] <Features of the embodiment> As described above, the magnetic refrigeration device (1) of this embodiment includes a storage unit (11), a magnetic field modulation unit (15), a first heat exchanger (16), a second heat exchanger (17), a heat medium circuit (C), and a reciprocating pump (21). The storage unit (11) has a magnetic working material (12) and an internal flow path (13) through which the heat medium flows and exchanges heat with the magnetic working material (12). The magnetic field modulation unit (15) applies a magnetic field fluctuation to the magnetic working material (12) in the storage unit (11) to induce a calorific 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 through the heat medium circuit (C) to the magnetic working material (12) in the storage unit (11) in response to the magnetic field fluctuation. The magnetic refrigeration device (1) performs a heating operation and a defrosting operation. In the heating operation, the heat medium heated by the magnetic working material (12) is released in the first heat exchanger (16), and the heat medium cooled by the magnetic working material (12) is absorbed in the second heat exchanger (17). In the defrosting operation, frost formed on the second heat exchanger (17) during the heating operation is removed. The magnetic working material (12) includes a plurality of materials (12a-12e) having different temperatures at which the calorific effect is maximized, and the plurality of materials (12a-12e) are arranged along the internal flow path (13) in the order of decreasing temperature.

[0048] In the magnetic refrigeration apparatus (1) of this embodiment, in the defrosting operation, the heat medium transport direction in the internal flow path (13) relative to the phase of the magnetic field fluctuation is switched to the opposite direction from that in the heating operation. This makes it possible to defrost the low-temperature side heat exchanger at low cost while avoiding an increase in the size of the high-temperature side heat exchanger or an increase in the complexity of the device structure due to the addition of a valve, a tank, or the like.

[0049] Specifically, in the magnetic refrigeration device (1) of this embodiment, in addition to the heat of the first heat exchanger (16) on the high-temperature side (indoor side in this example) as a heat source, losses due to the reversal of the AMR cycle (such as magnetic refrigeration cycle work, heat medium pressure loss, and eddy current loss) can also be used as a heat source, so there is no need to increase the size of the high-temperature heat exchanger or install a heat storage tank. Furthermore, the first heat exchanger (16) (indoor heat exchanger) can be made to have a lower temperature than the second heat exchanger (17) (outdoor heat exchanger) during defrost operation, and this temperature can be used as a heat source, so it is possible to avoid increasing the size of the indoor heat exchanger.

[0050] Furthermore, in the magnetic refrigeration apparatus (1) of this embodiment, the control unit (30) simply electrically controls the magnetic field modulation unit (15) and the reciprocating pump (21) to switch the heat transfer direction of the heat medium in the internal flow path (13) relative to the phase of the magnetic field fluctuation in the defrosting operation to the opposite direction from that in the heating operation. This offers the following advantages over a conventional method in which the high-temperature side and the low-temperature side are swapped by a valve-based flow path switching in the defrosting operation and defrosting is performed using heat generated by the magnetic working material. That is, when the magnetic refrigeration apparatus (1) of this embodiment transitions to the defrosting operation, the Curie temperatures of the materials in the cascaded magnetic working material (12) become close to the temperature of the heat medium, thereby increasing the amount of heat transfer and enabling rapid defrosting. In contrast, in a conventional method using a valve-based flow path switching, the Curie temperatures of the materials in the cascaded magnetic working material (12) differ significantly from the temperature of the heat medium at the time of transition to the defrosting operation, reducing the amount of heat transfer and potentially slowing down or even preventing defrosting.

[0051] In the magnetic refrigeration device (1) of this embodiment, the storage section (11) includes a plurality of partial storage sections (11a to 11e) connected in series to each other in the heat medium circuit (C), and each of the partial storage sections (11a to 11e) may contain at least one of the plurality of substances (12a to 12e). This increases the degree of freedom in the cascade arrangement of the solid refrigerant material (12).

[0052] In the magnetic refrigeration device (1) of this embodiment, the magnetic field modulation unit (15) and the reciprocating pump (21) may be electrically controlled to switch the heat medium transport direction in the internal flow path (13) according to the phase of the magnetic field fluctuation. In this way, defrosting can be performed by electrical control while avoiding an increase in the size and complexity of the device.

[0053] In the magnetic refrigeration device (1) of this embodiment, the frequency of the magnetic field fluctuation may be increased during the defrosting operation.

[0054] In this way, the frequency of the reciprocating transport of the heat medium increases along with the frequency of the magnetic field fluctuation, so the flow rate of the heat medium increases, increasing the pressure loss and the amount of heat transferred to the heat medium. Furthermore, eddy current loss increases in the materials constituting the housing portion (11) and the materials (such as the yoke) of the force field modulation portion (15) adjacent to the materials, further increasing the amount of heat transferred to the heat medium. This allows for faster defrosting.

[0055] In the magnetic refrigeration apparatus (1) of this embodiment, the flow rate of the heat medium in the heat medium circuit (C) may be increased during the defrosting operation.

[0056] In this way, the flow rate of the heat medium increases, and the pressure loss increases, resulting in an increase in the amount of heat transferred to the heat medium, thereby enabling the defrosting to be performed at a higher speed.

[0057] (Example) A defrosting simulation was performed on a magnetic refrigeration system (1) according to the present embodiment, in which 15 types of magnetic working materials (12) were arranged in cascade (15-stage cascade AMR). The simulation conditions were: RA (room air conditioning) 4 kW, low heating temperature (outdoor temperature: 2°C, indoor temperature: 20°C), 2 L of water (20°C) in the indoor heat exchanger and piping, 1.4 kg of ice on the outdoor heat exchanger (required heat of dissolution: 468 kJ), and no heat exchange with the indoor air in the indoor heat exchanger (fan off). The simulation results showed that the ice melted in approximately 70 seconds, and three minutes after the start of defrosting, the temperatures of the magnetic working materials (12) returned to near their Curie temperatures before the defrosting operation (i.e., during heating operation), allowing the heating operation to resume. When the operation mode is switched to defrost mode, the temperature of each material of the magnetic working material (12) begins to decrease. However, at the beginning of the operation mode switch, the temperature of each material is close to the Curie temperature, so that a large amount of heat is transferred to the heat medium in the internal flow path (13).

[0058] (Variation 1) Modification 1 will be described. The magnetic refrigeration apparatus (1) of this modification is a solid-state refrigeration apparatus that adjusts the temperature of a heat medium by utilizing the magnetocaloric effect, and is applied to, for example, an air conditioner. In this case, the magnetic refrigeration apparatus (1) adjusts the temperature of air in a space to be air-conditioned. The space to be air-conditioned is, for example, an indoor space. The magnetic refrigeration apparatus (1) switches between cooling operation, heating operation, and defrost operation.

[0059] <Configuration of magnetic refrigeration device> 8 and 9 are a piping diagram of the magnetic refrigeration apparatus (1) of this modified example and a schematic configuration diagram of the magnetic refrigeration unit (U), respectively. In Fig. 8 and Fig. 9, the same components as those in the magnetic refrigeration apparatus (1) of the embodiment shown in Fig. 1 are denoted by the same reference numerals.

[0060] As shown in Fig. 8, the magnetic refrigeration apparatus (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 one another via heat medium piping to form a heat medium circuit (C). Although not shown, the magnetic refrigeration apparatus (1) of this modification includes a control unit similar to the control unit (30) of the above embodiment.

[0061] As shown in FIG. 9, the magnetic refrigeration unit (U) mainly includes a storage section (11), a magnetic field modulation section (15) which is a force field modulation section, a reciprocating pump (21) which is a heat medium transport section, a first outlet pipe (41), a first inlet pipe (42), a second outlet pipe (43), a second inlet pipe (44), a first pump side piping (45), and a second pump side piping (46).

[0062] As in the previous embodiment, the storage section (11) has a magnetic working material (12) which is a solid refrigerant material, and an internal flow path (13) through which a heat transfer medium flows and exchanges heat with the solid refrigerant material (12). The magnetic working material (12) is made up of a plurality of materials (12a-12e) having different Curie temperatures at which the calorific effect is maximized, and the plurality of materials (12a-12e) are arranged along the internal flow path (13) in descending order of Curie temperature (i.e., in a cascade).

[0063] In this modification, a first internal flow path (13A) and a second internal flow path (13B) are formed inside the storage section (11) as the internal flow path (13). A first outlet pipe (41) is connected to one end of the first internal flow path (13A). A second inlet pipe (44) is connected to the other end of the first internal flow path (13A). A first inlet pipe (42) is connected to one end of the second internal flow path (13B). A second outlet pipe (43) is connected to the other end of the second internal flow path (13B).

[0064] The first outlet pipe (41) is provided with a first check valve (CV1). The first inlet pipe (42) is provided with a second check valve (CV2). The second outlet pipe (43) is provided with a third check valve (CV3). The second inlet pipe (44) is provided with a fourth check valve (CV4).

[0065] The first check valve (CV1) allows the heat medium to flow from the first internal flow path (13A) of the accommodating portion (11) toward the first heat exchanger (16) and prohibits the heat medium to flow in the opposite direction. The second check valve (CV2) allows the heat medium to flow from the first heat exchanger (16) toward the second internal flow path (13B) of the accommodating portion (11) and prohibits the heat medium to flow in the opposite direction. The third check valve (CV3) allows the heat medium to flow from the second internal flow path (13B) of the accommodating portion (11) toward the second heat exchanger (17) and prohibits the heat medium to flow in the opposite direction. The fourth check valve (CV4) allows the heat medium to flow from the second heat exchanger (17) toward the first internal flow path (13A) of the accommodating portion (11) and prohibits the heat medium to flow in the opposite direction.

[0066] As in the previous embodiment, the magnetic field modulation unit (15) applies a magnetic field fluctuation to the magnetic working material (12) in the container (11) to induce a calorific effect. The magnetic field modulation unit (15) is configured, for example, with an electromagnet capable of modulating a magnetic field. The magnetic field modulation unit (15) performs a first modulation operation and a second modulation operation. In the first modulation operation, a predetermined magnetic field is applied to the magnetic working material (22). In the second modulation operation, a magnetic field smaller than the predetermined magnetic field is applied or the predetermined magnetic field is removed.

[0067] As in the previous embodiment, the reciprocating pump (21) reciprocates the heat medium in the heat medium circuit (C). The reciprocating pump (21) is a piston pump. The reciprocating pump (21) includes a pump case (22), a piston (23), and a drive mechanism (not shown). The piston (23) is disposed inside the pump case (22). The piston (23) divides the interior of the pump case (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 case (22) is in communication with the first port (24), and the other chamber is in communication with the second port (25).

[0068] 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 first inlet pipe (42) on the upstream side of the second check valve (CV2). 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 second inlet pipe (44) on the upstream side of the fourth check valve (CV4).

[0069] The drive mechanism includes a rod connected to the piston (23), a crank connected to the rod, and an electric motor that drives the crank. When the electric motor drives and rotates the crank, the rod moves back and forth, causing the piston (23) to reciprocate within the pump case (22).

[0070] Specifically, the reciprocating pump (30) alternately performs a first transfer operation and a second transfer operation. In the first transfer operation (see FIGS. 10 and 11A), the piston (23) moves toward the first port (24). As a result, the heat transfer medium is discharged from the first port (24). The discharged heat transfer medium flows sequentially through the first inlet pipe (42), the second internal flow path (13B), and the second outlet pipe (43). In the second transfer operation (see FIGS. 10 and 11B), the piston (23) moves toward the second port (25). As a result, the heat transfer medium is discharged from the second port (25). The discharged heat transfer medium flows sequentially through the second inlet pipe (44), the first internal flow path (13A), and the first outlet pipe (41).

[0071] <Operation of magnetic refrigeration equipment> The magnetic refrigeration apparatus (1) of this modified example performs cooling operation, heating operation, and defrosting operation. In this modified example, the first heat exchanger (16) is an indoor heat exchanger that exchanges heat between the heat medium heated by the magnetic working material (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 material (12) and the outdoor air. That is, in the cooling operation, the air in the indoor space is cooled. The cooling operation corresponds to the cooling operation. In the heating operation, the air in the indoor space is heated. The heating operation corresponds to the heating operation. In the defrosting operation, the frost on the outdoor heat exchanger is melted.

[0072] In the cooling operation, the operation shown in FIG. 10(A) and the operation shown in FIG. 10(B) are alternately repeated.

[0073] 10A, the first modulation operation of the magnetic field modulation unit (15) and the first transfer operation 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 through the second outlet pipe (43). At the same time, the heat medium in the heat medium circuit (C) flows into the second port (25) of the pump case (22).

[0074] 10(B), the second modulation operation of the magnetic field modulation unit (15) and the second transfer operation 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 through the first outlet pipe (41). At the same time, the heat medium in the heat medium circuit (C) flows into the first port (24) of the pump case (22).

[0075] The heat medium heated by the magnetic refrigeration unit (U) in the operation shown in Fig. 10(A) flows through the second heat exchanger (17) as shown in Fig. 12. In the second heat exchanger (17), i.e., the outdoor heat exchanger, the heat medium dissipates heat to the outdoor air. The heat medium that has dissipated heat in the second heat exchanger (17) returns to the magnetic refrigeration unit (U).

[0076] The heat medium cooled by the magnetic refrigeration unit (U) in the operation shown in FIG. 10(B) flows through the first heat exchanger (16) as shown in FIG. 12. In the first heat exchanger (16), i.e., 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 has absorbed heat in the first heat exchanger (16) returns to the magnetic refrigeration unit (U).

[0077] For convenience, the flow of the heat medium in each operation is shown in the same diagram in Fig. 12. Furthermore, in Fig. 12, the first heat exchanger (16) and the second heat exchanger (17) from which the heat medium dissipates heat are hatched, and the heat exchanger from which the heat medium absorbs heat is dotted. This is also true in Figs. 13 and 14, which will be described later.

[0078] In the heating operation, the operation shown in FIG. 11(A) and the operation shown in FIG. 11(B) are alternately repeated.

[0079] 11(A), the second modulation operation of the magnetic field modulation unit (15) and the first transfer operation 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 through the second outlet pipe (43). At the same time, the heat medium in the heat medium circuit (C) flows into the second port (25) of the pump case (22).

[0080] 11(B), the first modulation operation of the magnetic field modulation unit (15) and the second transfer operation 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 through the first outlet pipe (41). At the same time, the heat medium in the heat medium circuit (C) flows into the first port (24) of the pump case (22).

[0081] The heat medium cooled by the magnetic refrigeration unit (U) in the operation shown in Fig. 11(A) flows through the second heat exchanger (17) as shown in Fig. 13. In the second heat exchanger (17), i.e., the outdoor heat exchanger, the heat medium absorbs heat from the outdoor air. The heat medium that has absorbed heat in the second heat exchanger (17) returns to the magnetic refrigeration unit (U).

[0082] The heat medium heated by the magnetic refrigeration unit (U) in the operation shown in FIG. 11(B) flows through the first heat exchanger (16) as shown in FIG. 13. In the first heat exchanger (16), i.e., the indoor heat exchanger, the heat medium dissipates heat to the indoor air. As a result, the indoor air is heated. The heat medium that dissipates heat in the first heat exchanger (16) returns to the magnetic refrigeration unit (U).

[0083] In the defrosting operation, the operation is basically the same as in the cooling operation, that is, the operation shown in FIG. 10(A) and the operation shown in FIG. 10(B) are alternately repeated.

[0084] The heat medium heated by the magnetic refrigeration unit (U) in the operation shown in Fig. 10(A) flows through the second heat exchanger (17) as shown in Fig. 14. In the second heat exchanger (17), i.e., the outdoor heat exchanger, the heat medium flowing therethrough melts the frost on the surface of the outdoor heat exchanger. The heat medium used to defrost the outdoor heat exchanger returns to the magnetic refrigeration unit (U).

[0085] The heat medium cooled by the magnetic refrigeration unit (U) in the operation shown in Fig. 10(B) flows through the first heat exchanger (16) as shown in Fig. 14. In the first heat exchanger (16), i.e., the indoor heat exchanger, the heat medium absorbs heat from the indoor air. The heat medium that has absorbed heat in the first heat exchanger (16) returns to the magnetic refrigeration unit (U).

[0086] <Features of Modification 1> As described above, in the magnetic refrigeration apparatus (1) of this modified example, in the defrosting operation, the heat medium transport direction in the internal flow path (13) relative to the phase of the magnetic field fluctuation is switched to the opposite direction to that in the heating operation, as in the above embodiment. This makes it possible to defrost the low-temperature side heat exchanger at low cost while avoiding an increase in the size of the high-temperature side heat exchanger or an increase in the complexity of the device structure due to the addition of a valve, a tank, or the like.

[0087] (Variation 2) A second modification will be described. The magnetic refrigeration apparatus (1) of this modification is a solid-state refrigeration apparatus that adjusts the temperature of a heat medium by utilizing the magnetocaloric effect, and is applied to, for example, an air conditioner. In this case, the magnetic refrigeration apparatus (1) adjusts the temperature of air in a space to be air-conditioned. The space to be air-conditioned is, for example, an indoor space. The magnetic refrigeration apparatus (1) switches between cooling operation, heating operation, and defrost operation.

[0088] <Configuration of magnetic refrigeration device> 15 and 16 are a piping diagram of the magnetic refrigeration apparatus (1) of this modified example and a schematic configuration diagram of the magnetic refrigeration unit (U), respectively. In Fig. 15 and Fig. 16, the same components as those in the magnetic refrigeration apparatus (1) of the embodiment shown in Fig. 1 are denoted by the same reference numerals.

[0089] 15, the magnetic refrigeration apparatus (1) mainly includes a magnetic refrigeration unit (U), a first heat exchanger (16), a second heat exchanger (17), a first four-way selector valve (F1), and a second four-way selector valve (F2). The magnetic refrigeration unit (U), the first heat exchanger (16), and the second heat exchanger (17) are connected to one another via heat medium piping to form a heat medium circuit (C). Although not shown, the magnetic refrigeration apparatus (1) of this modification has a control mechanism similar to the control unit (30) of the above embodiment.

[0090] As shown in FIG. 16 , the magnetic refrigeration unit (U) includes two magnetic refrigeration modules (10) as solid-state refrigeration modules, a low-temperature outlet pipe (51), a low-temperature inlet pipe (52), a high-temperature outlet pipe (53), a high-temperature inlet pipe (54), and a unit-side pump (55). The magnetic refrigeration unit (U) includes a first low-temperature three-way valve (56), a second low-temperature three-way valve (57), a first high-temperature three-way valve (58), and a second high-temperature three-way valve (59). The two magnetic refrigeration modules (10) include a first magnetic refrigeration module (10A) and a second magnetic refrigeration module (10B). In this modification, the unit-side pump (55) and the three-way valves (56, 57, 58, 59) form a heat medium transfer section (50).

[0091] Each of the first magnetic refrigeration module (10A) and the second magnetic refrigeration module (10B) has a container (11) and a magnetic field modulation section (15) that is a force field modulation section.

[0092] As in the previous embodiment, the storage section (11) has a magnetic working material (12) which is a solid refrigerant material, and an internal flow path (13) through which a heat transfer medium flows and exchanges heat with the solid refrigerant material (12). The magnetic working material (12) is made up of a plurality of materials (12a-12e) having different Curie temperatures at which the calorific effect is maximized, and the plurality of materials (12a-12e) are arranged along the internal flow path (13) in descending order of Curie temperature (i.e., in a cascade).

[0093] As in the previous embodiment, the magnetic field modulation unit (15) applies a magnetic field fluctuation to the magnetic working material (12) in the container (11) to induce a calorific effect. The magnetic field modulation unit (15) is configured, for example, with an electromagnet capable of modulating a magnetic field. The magnetic field modulation unit (15) performs a first modulation operation and a second modulation operation. In the first modulation operation, a predetermined magnetic field is applied to the magnetic working material (22). In the second modulation operation, a magnetic field smaller than the predetermined magnetic field is applied or the predetermined magnetic field is removed.

[0094] A first internal flow path (13A) and a second internal flow path (13B) are formed inside the housing (11) of each magnetic refrigeration module (10). A low-temperature end of the first internal flow path (13A) of the first magnetic refrigeration module (10A) is connected to a low-temperature outlet pipe (51) via a first low-temperature three-way valve (56). A low-temperature end of the second internal flow path (13B) of the first magnetic refrigeration module (10A) is connected to a low-temperature inlet pipe (52) via a second low-temperature three-way valve (57). A high-temperature end of the first internal flow path (13A) of the second magnetic refrigeration module (10B) is connected to a high-temperature inlet pipe (54) via a second high-temperature three-way valve (59). A high-temperature end of the second internal flow path (13B) of the second magnetic refrigeration module (10B) is connected to a high-temperature outlet pipe (53) via a first high-temperature three-way valve (58).

[0095] The unit-side pump (55) is provided in the high-temperature outlet pipe (53). The unit-side pump (55) is a one-way pump. The unit-side pump (55) transports the heat medium toward the downstream side of the high-temperature outlet pipe (53).

[0096] A first port of the low-temperature first three-way valve (56) communicates with the low-temperature outflow pipe (51). A second port of the low-temperature first three-way valve (56) communicates with the low-temperature end of the first internal flow path (13A) of the second magnetic refrigeration module (10B). A third port of the low-temperature first three-way valve (56) communicates with the low-temperature end of the first internal flow path (13A) of the first magnetic refrigeration module (10A).

[0097] A first port of the low-temperature second three-way valve (57) communicates with the low-temperature inlet pipe (52). A second port of the low-temperature second three-way valve (57) communicates with the low-temperature end of the second internal flow path (13B) of the second magnetic refrigeration module (10B). A third port of the low-temperature second three-way valve (57) communicates with the low-temperature end of the second internal flow path (13B) of the first magnetic refrigeration module (10A).

[0098] A first port of the high-temperature first three-way valve (58) communicates with the high-temperature outflow pipe (53). A second port of the high-temperature first three-way valve (58) communicates with the high-temperature end of the second internal flow path (13B) of the second magnetic refrigeration module (10B). A third port of the high-temperature first three-way valve (58) communicates with the high-temperature end of the second internal flow path (13B) of the first magnetic refrigeration module (10A).

[0099] A first port of the high-temperature second three-way valve (59) communicates with the high-temperature inlet pipe (54). A second port of the high-temperature second three-way valve (59) communicates with the high-temperature end of the first internal flow path (13A) of the second magnetic refrigeration module (10B). A third port of the high-temperature second three-way valve (59) communicates with the high-temperature end of the first internal flow path (13A) of the first magnetic refrigeration module (10A).

[0100] Each of the three-way valves (56, 57, 58, 59) has a first port, a second port, and a third port. In the drawings, the first port of the three-way valve is represented by a circled 1, the second port of the three-way valve is represented by a circled 2, and the third port of the three-way valve is represented by a circled 3.

[0101] Each three-way valve (56, 57, 58, 59) switches between a first state (the state indicated by the solid line in FIG. 16) and a second state (the state indicated by the dashed line in FIG. 16). In the first state, each three-way valve (56, 57, 58, 59) connects the first port with the second port. In the second state, each three-way valve (56, 57, 58, 59) connects the first port with the third port.

[0102] In this modification, the first heat exchanger (16) shown in FIG. 15 is an indoor heat exchanger that exchanges heat between the heat medium and the indoor air. One end of the first heat exchanger (16) is connected to the second port of the first four-way selector valve (F1) via a pipe. The other end of the first heat exchanger (16) is connected to the second port of the second four-way selector valve (F2) via a pipe. The second heat exchanger (17) shown in FIG. 15 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 port of the first four-way selector valve (F1) via a pipe. The other end of the second heat exchanger (17) is connected to the third port of the second four-way selector valve (F2) via a pipe.

[0103] The first four-way switching valve (F1) and the second four-way switching valve (F2) are switching mechanisms that switch the flow path of the heat medium in the heat medium circuit (C). The first four-way switching valve (F1) and the second four-way switching valve (F2) of this modification switch the flow path of the heat medium during cooling, heating, and defrosting operations. Each of the four-way switching valves (F1, F2) has a first port, a second port, a third port, and a fourth port. In the drawings, the first port of the four-way switching valve is indicated by a circled number 1, the second port of the four-way switching valve is indicated by a circled number 2, the third port of the four-way switching valve is indicated by a circled number 3, and the fourth port of the four-way switching valve is indicated by a circled number 4.

[0104] Each four-way switching valve (F1, F2) switches between a first state (a state indicated by a solid line in FIG. 15) and a second state (a state indicated by a dashed line in FIG. 15). In the first state, each four-way switching valve (F1, F2) communicates between the first port and the second port, and also communicates between the third port and the fourth port. In the second state, each four-way switching valve (F1, F2) communicates between the first port and the third port, and also communicates between the second port and the fourth port.

[0105] A first port of the first four-way selector valve (F1) communicates with the high-temperature inlet pipe (54). A second port of the first four-way selector valve (F1) communicates with the first heat exchanger (16). A third port of the first four-way selector valve (F1) communicates with the second heat exchanger (17). A fourth port of the first four-way selector valve (F1) communicates with the low-temperature inlet pipe (52).

[0106] A first port of the second four-way selector valve (F2) communicates with the high-temperature outlet pipe (53). A second port of the second four-way selector valve (F2) communicates with the first heat exchanger (16). A third port of the second four-way selector valve (F2) communicates with the second heat exchanger (17). A fourth port of the second four-way selector valve (F2) communicates with the low-temperature outlet pipe (51).

[0107] The control unit (30) of this modification is connected to the magnetic refrigeration unit (U) and the four-way selector valves (F1, F2) via communication lines. That is, the control unit (30) controls the magnetic field modulation unit (15), the heat medium transfer unit (50), and the four-way selector valves (F1, F2).

[0108] <Operation of magnetic refrigeration equipment> The magnetic refrigeration apparatus (1) of this modified example performs cooling operation, heating operation, and defrosting operation. In this modified example, the first heat exchanger (16) is an indoor heat exchanger that exchanges heat between the heat medium heated by the magnetic working material (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 material (12) and the outdoor air. That is, in the cooling operation, the air in the indoor space is cooled. The cooling operation corresponds to the cooling operation. In the heating operation, the air in the indoor space is heated. The heating operation corresponds to the heating operation. In the defrosting operation, the frost on the outdoor heat exchanger is melted.

[0109] In the cooling operation, the operation shown in Fig. 17(A) and the operation shown in Fig. 17(B) are alternately repeated, with the cycle of switching between the operations being about one second.

[0110] 17A, the first magnetic refrigeration module (10A) performs the first modulation operation, and the second magnetic refrigeration module (10B) performs the second modulation operation. The first low-temperature three-way valve (56) is set to the first state, the second low-temperature three-way valve (57) is set to the second state, the first high-temperature three-way valve (58) is set to the second state, and the second high-temperature three-way valve (59) is set to the first state. The unit-side pump (55) operates.

[0111] 17(B), the first magnetic refrigeration module (10A) performs the second modulation operation, and the second magnetic refrigeration module (10B) performs the first modulation operation. The first low-temperature three-way valve (56) is set to the second state, the second low-temperature three-way valve (57) is set to the first state, the first high-temperature three-way valve (58) is set to the first state, and the second high-temperature three-way valve (59) is set to the second state. The unit-side pump (55) operates.

[0112] In the cooling operation, as shown in FIG. 18 , the first four-way selector valve (F1) is set to the second state, and the second four-way selector valve (F2) is set to the second state. This forms a flow path in which the heat medium cooled by each magnetic refrigeration module (10) flows through the low-temperature outlet pipe (51), the first heat exchanger (16), and the low-temperature inlet pipe (52), and the heat medium heated by each magnetic refrigeration module (10) flows through the high-temperature outlet pipe (53), the second heat exchanger (17), and the high-temperature inlet pipe (54). For convenience, FIG. 18 shows the heat medium flow in each operation in the same diagram. In FIG. 18 , the first heat exchanger (16) and the second heat exchanger (17) from which the heat medium releases heat are hatched, and the heat exchanger from which the heat medium absorbs heat are dotted. This is also true in FIGS. 19 and 20 , which will be described later.

[0113] Specifically, the heat medium heated by the magnetic refrigeration unit (U) passes through the second four-way selector valve (F2) and flows through the second heat exchanger (17). In the second heat exchanger (17), i.e., the outdoor heat exchanger, the heat medium dissipates heat to the outdoor air. The heat medium that has dissipated heat in the second heat exchanger (17) passes through the first four-way selector valve (F1) and returns to the magnetic refrigeration unit (U).

[0114] The heat medium cooled by the magnetic refrigeration unit (U) passes through the second four-way selector valve (F2) and flows through the first heat exchanger (16). In the first heat exchanger (16), i.e., 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 has absorbed heat in the first heat exchanger (16) passes through the first four-way selector valve (F1) and returns to the magnetic refrigeration unit (U).

[0115] In the heating operation, the operation shown in Fig. 17(A) and the operation shown in Fig. 17(B) are alternately repeated. In the heating operation, as shown in Fig. 19, the first four-way selector valve (F1) is set to the first state, and the second four-way selector valve (F2) is set to the first state. This forms "a flow path in which the heat medium heated by each magnetic refrigeration module (10) flows through the high-temperature outlet pipe (53), the first heat exchanger (16), and the high-temperature inlet pipe (54), and the heat medium cooled by each magnetic refrigeration module (10) flows through the low-temperature outlet pipe (51), the second heat exchanger (17), and the low-temperature inlet pipe (52)."

[0116] Specifically, the heat medium cooled by the magnetic refrigeration unit (U) passes through the second four-way selector valve (F2) and flows through the second heat exchanger (17). In the second heat exchanger (17), i.e., the outdoor heat exchanger, the heat medium absorbs heat from the outdoor air. The heat medium that has absorbed heat in the second heat exchanger (17) passes through the first four-way selector valve (F1) and returns to the magnetic refrigeration unit (U).

[0117] The heat medium heated by the magnetic refrigeration unit (U) passes through the second four-way selector valve (F2) and flows through the first indoor heat exchanger (16). In the first indoor heat exchanger (16), i.e., the indoor heat exchanger, the heat medium dissipates heat into the indoor air. As a result, the indoor air is heated. The heat medium that has dissipated heat in the first indoor heat exchanger (16) passes through the first four-way selector valve (F1) and returns to the magnetic refrigeration unit (U).

[0118] In the defrosting operation, the operation is substantially the same as that in the cooling operation. That is, in the defrosting operation, the operation shown in FIG. 17(A) and the operation shown in FIG. 17(B) are alternately repeated. The cycle of switching between the operations is about one second. The defrosting operation is executed, for example, during the heating operation in winter, when the conditions for frost formation on the surface of the second heat exchanger (17), i.e., the outdoor heat exchanger, are met.

[0119] In the defrosting operation, the first four-way switching valve (F1) is set to the second state, and the second four-way switching valve (F2) is set to the second state, as shown in Fig. 20. This forms "a flow path in which the heat medium cooled by each magnetic refrigeration module (10) flows through the low-temperature outlet pipe (51), the first heat exchanger (16), and the low-temperature inlet pipe (52), and the heat medium heated by each magnetic refrigeration module (10) flows through the high-temperature outlet pipe (53), the second heat exchanger (17), and the high-temperature inlet pipe (54)."

[0120] Specifically, the heat medium heated by the magnetic refrigeration unit (U) passes through the second four-way selector valve (F2) and flows into the second heat exchanger (17). In the second heat exchanger (17), i.e., the outdoor heat exchanger, the heat medium flowing therethrough melts the frost on the surface of the outdoor heat exchanger. The heat medium used to defrost the outdoor heat exchanger passes through the first four-way selector valve (F1) and returns to the magnetic refrigeration unit (U).

[0121] The heat medium cooled by the magnetic refrigeration unit (U) passes through the second four-way selector valve (F2) and flows through the first heat exchanger (16). In the first heat exchanger (16), i.e., the indoor heat exchanger, the heat medium absorbs heat from the indoor air. The heat medium that has absorbed heat in the first heat exchanger (16) passes through the first four-way selector valve (F1) and returns to the magnetic refrigeration unit (U).

[0122] <Features of Modification 2> When the cooling operation (cooling operation) is not required, the piping system shown in Fig. 19 may be configured without the four-way switching valves (F1, F2), and in the defrost operation, the magnetic field modulation unit (15) and the heat medium transfer unit (50) may be electrically controlled to switch the heat medium transfer direction in the internal flow path (13) relative to the phase of the magnetic field fluctuation to the opposite direction from that in the heating operation (heating operation) in the operation shown in Fig. 17(A) and (B). This makes it possible to defrost the low-temperature side heat exchanger at low cost while avoiding an increase in the size of the high-temperature side heat exchanger or a complication of the device structure due to the addition of a valve, a tank, or the like.

[0123] (Variation 3) A third modification will now be described. The magnetic refrigeration apparatus (1) of this modification is a solid-state refrigeration apparatus that adjusts the temperature of a heat medium by utilizing the magnetocaloric effect, and is applied to, for example, an air conditioner. In this case, the magnetic refrigeration apparatus (1) adjusts the temperature of air in a space to be air-conditioned. The space to be air-conditioned is, for example, an indoor space.

[0124] <Configuration of magnetic refrigeration device> In the magnetic refrigeration device (1) of the embodiment and the first and second modifications, a magnetic working material (12) is filled inside a storage section (11) formed of a hollow case or column, and a magnetic field modulation section (15) formed of an electromagnet capable of modulating a magnetic field is used to impart a magnetic field fluctuation to the magnetic working material (12) inside the storage section (11).

[0125] In contrast, the magnetic refrigeration apparatus (1) of this modified example is a magnetic heat pump apparatus in which a magnetic circuit rotates. Specifically, as shown in FIG. 21 , the magnetic refrigeration apparatus (1) of this modified example includes a heat medium circuit (C) that mainly includes 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 heat medium piping. The magnetic refrigeration apparatus (1) is a solid-state refrigeration apparatus that adjusts the temperature of the heat medium by utilizing the calorific effect, and the magnetic refrigeration module (10) is a solid-state refrigeration module that adjusts the temperature of the heat medium by utilizing the calorific effect.

[0126] The magnetic refrigeration module (10) is provided, for example, in an air conditioner that exchanges heat with a secondary refrigerant, air, etc. The use of the magnetic refrigeration module (10) is not limited thereto, and the magnetic refrigeration module (10) may be provided, for example, in a magnetic refrigeration system (1) configured as a chiller for cooling only.

[0127] The magnetic refrigeration module (10) includes an annular container (11) having a plurality of partial containers (11a-11l) that contain a magnetically active material (12) as a solid refrigerant material and form an internal flow path (13) through which a heat transfer medium flows. The magnetic refrigeration module (10) generates a magnetocaloric effect by applying or removing a magnetic field, which is a force field, to the magnetically active material (12), thereby heating or cooling the heat transfer medium flowing through the flow path (13).

[0128] In this modified example, the magnetic working material (12) is also composed of a plurality of substances (12a to 12e) with different Curie temperatures at which the calorific effect is maximized, and the plurality of substances (12a to 12e) are arranged along the internal flow path (13) of each partial storage section (11a to 11l) in order of decreasing Curie temperature (i.e., in a cascade).

[0129] As shown in FIGS. 21 and 22, the magnetic refrigeration module (10) is composed of a plurality of unit modules (10a-10l), for example, twelve. The components of the plurality of unit modules (10a-10l) are housed in a plurality of partial housing sections (11a-11l), respectively. In this embodiment, each of the partial housing sections (11a-11l) has, for example, an annular sector shape, but is not limited thereto and may have a sector shape, a trapezoidal shape, or the like. The plurality of partial housing sections (11a-11l) are combined in an annular shape to form the annular housing section (11) of the magnetic refrigeration module (10). The thickness of each of the partial housing sections (11a-11l) is set to a thickness that makes it difficult for magnetic flux leakage to occur and that ensures the required volume of the housing section. In the following description, when the term "partial storage section (11a)" is used, it refers to any storage section piece among the multiple partial storage sections (11a to 11l), and when the term "unit module (10a)" is used, it refers to any unit module among the multiple unit modules (10a to 10l).

[0130] In this modification, as shown in FIGS. 22 and 23 , a magnetic field modulation unit (15) serving as a force field modulation unit is arranged to sandwich the magnetic refrigeration module (10) in the axial direction of the annular housing unit (11). The magnetic field modulation unit (15) includes an annular magnet (15a) serving as a force field generator arranged adjacent to the magnetic refrigeration module (10), a yoke (15b) for supporting the annular magnet (15a) and forming a magnetic path, and a rotation mechanism (15c). The rotation mechanism (15c) is arranged to extend in the axial direction of the annular housing unit (11) through a central opening of the magnetic refrigeration module (10). The magnet (15a) is rotated in the circumferential direction of the annular housing unit (11) by the rotation mechanism (15c). The number of magnets (15a) (a pair of magnets sandwiching the magnetic refrigeration module (10) in the axial direction of the annular housing unit (11)) is equal to the number of poles of the magnetic circuit. In this example, two magnets (15a) are arranged so as to overlap an area equivalent to three partial accommodating sections (11a). In this example, the magnets (15a) and the unit modules (20a) are arranged evenly in the circumferential direction of the same axis. The annular accommodating section (11), i.e., the magnetic refrigeration module (10), may be fixed.

[0131] In the magnetic refrigeration module (10) of this modification, the unit modules (10a) excited by the magnet (15a) change from moment to moment as the rotation mechanism (15c) rotates, thereby forming a magnet-rotating magnetic refrigeration module (10). Note that Figures 21 and 22 show the unit modules (10a, 10b, 10c, 10g, 10h, 10i) as being magnetized and the unit modules (10d, 10e, 10f, 10j, 10k, 10l) as being demagnetized.

[0132] As shown in FIG. 21, each of the unit modules (10a-10l) constituting the magnetic refrigeration module (10) has a low-temperature inlet channel (61), a low-temperature outlet channel (62), a high-temperature inlet channel (63), and a high-temperature outlet channel (64). The inlet channels (61, 63) and outlet channels (62, 64) communicate with the internal flow paths (13) of the partial accommodating sections (11a-11l) of the unit modules (10a-10l). The heat medium flowing in from the low-temperature inlet channel (61) flows through the internal flow path (13) of the partial accommodating section (11a) and is discharged from the high-temperature outlet channel (64). The heat medium flowing in from the high-temperature inlet channel (63) flows through the internal flow path (13) of the partial accommodating section (11a) and is discharged from the low-temperature outlet channel (62).

[0133] 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 indoor air. The first heat exchanger (16) has a first outlet (16a) connected to the high-temperature inlet channel (63) of the magnetic refrigeration module (10) and a first inlet (16b) connected to the high-temperature outlet channel (64) of the magnetic refrigeration module (10). A high-pressure multi-way switching valve (110) is provided in the heat medium piping between the first outlet (16a) and the high-temperature inlet channel (63) of each unit module (10a-10l). A low-pressure multi-way switching valve (120) is provided in the heat medium piping between the first inlet (16b) and the high-temperature outlet channel (64) of each unit module (10a-10l). In this modification, a high-pressure side multi-way switching valve (110) and a low-pressure side multi-way switching valve (120) are integrated to form a rotary valve type multi-way switching valve (100).

[0134] In this modification, 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 outdoor air. The second heat exchanger (17) has a second outlet (17a) connected to the low-temperature inlet channel (61) of the magnetic refrigeration module (10) and a second inlet (17b) connected to the low-temperature outlet channel (62) of the magnetic refrigeration module (10). A first check valve (91) is provided in the heat medium piping between the second outlet (17a) and the low-temperature inlet channel (61) of each unit module (10a-10l). A second check valve (92) is provided in the heat medium piping between the second inlet (17b) and the low-temperature outlet channel (62) of each unit module (10a-10l).

[0135] The heat medium pump (21A) is for circulating a heat medium between the magnetic refrigeration module (10) and each of the heat exchangers (60, 70). The heat medium pump (21A) is provided, for example, in a heat medium pipe between the low-pressure side multi-way switching valve (120) of the rotary valve type multi-way switching valve (100) and the second heat exchanger (17).

[0136] In this modification, the heat medium pump (21A) and the rotary valve type multi-way selector valve (100) form a heat medium transfer section.

[0137] <Operation of magnetic refrigeration equipment> In the magnetic refrigeration system (1) shown in FIG. 21, the check valves (91, 92) and the rotary valve type multi-way switching valve (100) are controlled, and a magnetic field is applied to or removed from the accommodation section (11) of the magnetic refrigeration module (10) (unit modules (10a to 10l)) in accordance with the control operation, thereby supplying cold.

[0138] Hereinafter, a specific description will be given of an example in which the unit modules (20a, 20b, 20c, 20g, 20h, 20i) are magnetized and the unit modules (20d, 20e, 20f, 20j, 20k, 20l) are demagnetized, as shown in Figures 21 and 22. In Figure 21, the flow of the heat medium is indicated by arrows.

[0139] First, the heat medium flowing out from the second outlet portion (17a) of the second heat exchanger (17) selectively flows into the low-temperature side inlet passage (61) of the magnetized unit module (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 material (12) in the exothermic state in the unit module (10a, 10b, 10c, 10g, 10h, 10i), and then flows out from the high-temperature side outlet passage (64).

[0140] The heat medium flowing out from the high-temperature side outlet passage (64) of the unit modules (10a, 10b, 10c, 10g, 10h, 10i) passes through the heat medium pump (21A) and flows into the first inlet (16b) of the first heat exchanger (16) under the control of the low-pressure side multi-way selector valve (120). The heat medium exchanges heat with a secondary refrigerant flowing in a heat source unit (not shown), such as a cooling tower, and flows out from the first outlet (16a) of the first heat exchanger (16).

[0141] The heat medium flowing out from the first outlet portion (16a) of the first heat exchanger (16) selectively flows into the high-temperature side inlet passage (63) of the demagnetized unit module (10d, 10e, 10f, 10j, 10k, 10l) under the control of the high-pressure side multi-way switching valve (110). The heat medium is cooled by heat exchange with the magnetic working material (12) in an endothermic state in the unit module (10d, 10e, 10f, 10j, 10k, 10l), and then flows out from the low-temperature side outlet passage (62).

[0142] The heat medium flowing out from the low-temperature side outlet passage (62) of the unit modules (10d, 10e, 10f, 10j, 10k, 10l) flows into the second inlet (17b) of the second heat exchanger (17) by control of the second check valve (92). The heat medium exchanges heat with a secondary refrigerant flowing through a utilization unit (not shown), such as an air handling unit, and flows out from the second outlet (17a) of the second heat exchanger (17).

[0143] <Features of Modification 3> In the heating operation of this modified example, the above-described heat medium flow control is repeatedly performed while selectively switching the unit modules (10a) to be magnetized or demagnetized by the magnetic field modulation unit (15). Furthermore, if conditions for frost formation on the surface of the low-temperature side heat exchanger (second heat exchanger (17)) are met during the heating operation, a defrost operation is performed. In the defrost operation, the heat medium transport direction in the internal flow path (13) relative to the phase of the magnetic field fluctuation is switched to the opposite direction from that in the heating operation, for example, by electrically controlling the magnetic field modulation unit (15) and the rotary valve type multi-way selector valve (100). This allows defrosting of the low-temperature side heat exchanger at low cost while avoiding an increase in the size of the high-temperature side heat exchanger or a complication of the device structure due to the addition of valves, tanks, etc.

[0144] (Variation 4) In the magnetic refrigeration device (1) of the embodiment and the first to third modifications, the magnetic field modulation unit (15) and the heat medium transport unit, i.e., the reciprocating pump (21) and various valves, are driven independently of each other and electrically synchronized with each other, and the heat medium transport direction in the internal flow path (13) is electrically switched in accordance with the phase of the magnetic field fluctuation.

[0145] In contrast, in this modified example, a phase adjustment mechanism such as a shaft, a belt, or a gear is used to drive the magnetic field modulation unit (15) in conjunction with the reciprocating pump (21) serving as the heat medium transport unit and various valves, and 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) according to the phase of the magnetic field fluctuation.

[0146] <Configuration of magnetic refrigeration device> Fig. 24 is a schematic diagram of the main components of the magnetic refrigeration device (1) of this modified example. In Fig. 24, the same components as those of the magnetic refrigeration device (1) of the modified example 3 shown in Figs. 21 to 23 are denoted by the same reference numerals.

[0147] As shown in FIG. 24, in the magnetic refrigeration device of this modification, the rotary magnetic circuit (magnetic field modulation section (15)) in the magnetic refrigeration device (1) of the third modification is connected to the rotary valve type multi-way switching valve (100) via a connecting shaft (71), thereby achieving timing (synchronization) between the magnetic field fluctuation and the heat medium flow.

[0148] In the rotary valve type multi-way switching valve (100) shown in Figures 24 to 26, a high-pressure side multi-way switching valve (110) and a low-pressure side multi-way switching valve (120) are integrally provided in the same valve box (101). In Figure 24, the flow of the heat medium is indicated by arrows.

[0149] The rotary valve type multi-way selector valve (100) mainly includes a valve body (101), a rotary shaft (102), a high-pressure side inlet port (115), a low-pressure side outlet port (125), a high-pressure side valve plate (111), a high-pressure side valve element (112), a low-pressure side valve plate (121), and a low-pressure side valve element (122). The valve body (101) is made of, for example, an acrylic resin. The rotary shaft (102) is made of, for example, stainless steel. The high-pressure side valve plate (111) and the low-pressure side valve plate (121) are made of, for example, aluminum. The high-pressure side valve element (112) and the low-pressure side valve element (122) are made of, for example, a fluororesin such as PTFE.

[0150] In this modification, the "axial direction" refers to the direction in which the rotation shaft (102) (axial center (J)) extends, the "radial direction" refers to the direction perpendicular to the rotation shaft (102), and the "circumferential direction" refers to the circumferential direction of a circle centered on the rotation shaft (102). The same applies to modification 5, which will be described later.

[0151] A high-pressure side valve plate (111) is disposed at one axial end (upper end in FIG. 24) of the valve box (101). A low-pressure side valve plate (121) is disposed at the other axial end (lower end in FIG. 24) of the valve box (101). A high-pressure side valve element (112) is disposed inside the high-pressure side valve plate (111) of the valve box (101). A low-pressure side valve element (122) is disposed inside the low-pressure side valve plate (121) of the valve box (101).

[0152] The rotating shaft (102) extends from the outside to the inside of the valve body (101) so as to penetrate the center of the high-pressure side valve plate (111). The rotating shaft (102) is rotated by a drive rotation mechanism (not shown). A seal member (103), such as a mechanical seal, is provided between the rotating shaft (102) and the high-pressure side valve plate (111). A high-pressure side valve disc (112) and a low-pressure side valve disc (122) are attached to the rotating shaft (102) inside the valve body (101). The high-pressure side valve disc (112) and the low-pressure side valve disc (122) are rotatable together with the rotating shaft (102).

[0153] The high-pressure side valve element (112) and the low-pressure side valve element (122) are rotationally driven on the same rotation shaft (102). Therefore, the high-pressure side valve element (112) and the low-pressure side valve element (122) rotate in the same direction at the same rotation speed. Furthermore, the relative positional relationship between the high-pressure side valve element (112) and the low-pressure side valve element (122) does not change with rotation.

[0154] The high-pressure side inlet port (115) is disposed on a radial side of the valve body (101). As a result, the interior of the valve body (101) is maintained at high pressure by communicating with the high-pressure side inlet port (115). The low-pressure side outlet port (125) is disposed in the center of the low-pressure side valve plate (121).

[0155] The high-pressure-side valve plate (111) is formed with a plurality of high-pressure-side outlet ports (113) surrounding the rotary shaft (102). The high-pressure-side valve element (112) is formed with a high-pressure-side flow path (114). The high-pressure-side flow path (114) has an open structure to the interior of the valve body (101). The high-pressure-side flow path (114) connects to at least one port (113a) of the plurality of high-pressure-side outlet ports (113) depending on the rotational position of the high-pressure-side valve element (112), selectively communicating the port (113a) with the high-pressure-side inlet port (115). The high-pressure-side valve element (112) closes at least one port (113b) of the plurality of high-pressure-side outlet ports (113) that has a pressure lower than the pressure inside the valve body (101) depending on the rotational position. Due to the pressure difference between the port (113b) and the inside of the valve box (101), the high-pressure side valve element (112) is attracted to the high-pressure side valve plate (111) and tightly adheres to it, thereby preventing fluid leakage.

[0156] The high-pressure-side valve element (112) 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 section of the rotating shaft (102) perpendicular to the axial direction may be D-shaped, and a through-hole of the same D shape may be formed in the high-pressure-side valve element (112). The rotating shaft (102) may be passed through the through-hole, thereby fixing the high-pressure-side valve element (112) in the circumferential direction of the rotating shaft (102) and making it movable in the axial direction of the rotating shaft (102). This makes it possible to prevent the rotating shaft (102) from being sucked in when the high-pressure-side valve element (112) is sucked toward the high-pressure-side valve plate (111).

[0157] The low-pressure side valve plate (121) is formed with a plurality of low-pressure side inlet ports (123) surrounding a low-pressure side outlet port (125). The low-pressure side valve element (122) is formed with a low-pressure side flow path (124). The low-pressure side valve element (122) closes at least one port (123a) of the plurality of low-pressure side inlet ports (123) that is at a high pressure depending on its rotational position. The low-pressure side flow path (124) is connected to at least one port (123b) that is at a lower pressure than the pressure inside the valve box (101) depending on the rotational position of the low-pressure side valve element (122), and selectively communicates the port (123b) with the low-pressure side outlet 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 in the low-pressure side flow path (124) (inside the low-pressure side valve element (122)). As a result, the low-pressure side valve element (122) is attracted to the low-pressure side valve plate (121) and tightly adheres to it due to the pressure difference between the inside of the low-pressure side valve element (122) and the inside of the valve box (101), thereby preventing fluid leakage.

[0158] The low-pressure side valve element (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 section of the rotating shaft (102) perpendicular to the axial direction may be D-shaped, and a through-hole of the same D shape may be formed in the low-pressure side valve element (122). The rotating shaft (102) may be passed through the through-hole, thereby fixing the low-pressure side valve element (122) in the circumferential direction of the rotating shaft (102) and making it movable in the axial direction of the rotating shaft (102). This makes it possible to prevent the rotating shaft (102) from being sucked in when the low-pressure side valve element (122) is sucked toward the low-pressure side valve plate (121).

[0159] As described above, the high-pressure-side valve element (112) and the low-pressure-side valve element (122) are configured as separate members and can move independently in the axial direction (slidable relative to the rotation shaft (102)), so that the suction forces acting on the high-pressure-side valve element (112) and the low-pressure-side valve element (122) do not cancel each other out. Furthermore, because the valve elements (112, 122) can move in the axial direction, when the spring (104) is installed between the valve elements (112, 122), the elastic force of the spring (104) can bring the valve elements (112, 122) into close contact with the valve plates (111, 121).

[0160] The low-pressure side valve element (122) may 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 element (122) may be made of a thermal insulating material. The thermal insulating material may be a resin with low friction and excellent sliding properties, such as PTFE or POM.

[0161] In the heat medium circuit (C) shown in FIG. 21 , the high-pressure side outlet port (113) of the high-pressure side multi-way switching valve (110) is connected to the high-temperature side inlet passage (63) of the magnetic refrigeration module (10) (unit modules (10a-10l)). The low-pressure side inlet port (123) of the low-pressure side multi-way switching valve (120) is connected to the high-temperature side outlet passage (64) of the magnetic refrigeration module (10). The high-pressure side outlet port (113) and the low-pressure side inlet port (123) connected to the same unit module (10a-10l) are never open at the same time. Specifically, when one of the high-pressure side outlet port (113) and the low-pressure side inlet port (123) connected to the same unit module (10a-10l) is open, the other is closed; and when one of the high-pressure side outlet port (113) and the low-pressure side inlet port (123) is closed, the other is open or closed.

[0162] Incidentally, when the internal pressure of the valve box (101) is low immediately after the magnetic refrigeration device (1) starts operating, or when the valve disc (112, 122) is pressed against the valve plate (111, 121) in a direction opposite to the direction of gravity to bring the valve disc (112, 122) into tight contact with the valve plate (111, 121), the contact force may be insufficient, resulting in fluid leakage.

[0163] Therefore, the spring (104) is additionally disposed inside the valve box (101) to increase the contact force between the valve discs (112, 122) and the valve plates (111, 121). During normal operation of the magnetic refrigeration device (1), the contact force is generated by utilizing the high pressure inside the valve box (101). Therefore, the elastic force of the spring (104) is sufficient to weakly bring the valve discs (112, 122) into contact with the valve plates (111, 121). This makes it possible to suppress wear of the valve discs (112, 122) caused by the elastic force of the spring (104).

[0164] Specifically, the spring (104) is disposed between the high-pressure-side valve element (112) and the low-pressure-side valve element (122). The spring (104) extends in the axial direction while surrounding the outer periphery of the rotary shaft (102). One end of the spring (104) is attached to the high-pressure-side valve element (112), and the other end of the spring (104) is attached to the low-pressure-side valve element (122). In this configuration, the installation of the spring (104) makes it possible to press the high-pressure-side valve element (112) against the high-pressure-side valve plate (111) and press the low-pressure-side valve element (122) against the low-pressure-side valve plate (121) without providing any other member such as a spring retainer. Furthermore, 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, 122) or between the spring (104) and the valve box (101), thereby avoiding the occurrence of friction torque and wear.

[0165] <Features of Variation 4> In the magnetic refrigeration device (1) of this modification, the shaft (rotation mechanism (15c)) of the magnetic field modulation unit (15) and the rotary shaft (102) of the rotary valve type multi-way switching valve (100) are connected via a connecting shaft (71), so that the magnetic field modulation unit (15) and the rotary valve valve elements (high-pressure side valve element (112) and low-pressure side valve element (122)) rotate on the same axis (hereinafter referred to as a common axis). On the other hand, the magnetic refrigeration module (10) is fixed.

[0166] Normally, the main body (valve box (101), valve plates (high-pressure side valve plate (111), low-pressure side valve plate (121))) of the rotary valve type multi-way selector valve (100) is fixed, but in this modified example, the main body of the rotary valve type multi-way selector valve (100) is rotated around a common axis. As a result, the port positions of the valve plates (high-pressure side valve plate (111), low-pressure side valve plate (121)) move in the rotational direction, making it possible to change the timing of the heat medium flow (i.e., shift the phase).

[0167] The rotary valve type multi-way switching valve (100) is connected to the magnetic refrigeration module (10), the heat medium pump (21A), and the like by piping, and the use of flexible piping (e.g., plastic tubing) allows the rotary valve type multi-way switching valve (100) body to be easily rotated. The rotation angle for phase adjustment is usually within ±90° when a two-pole magnet (15a) is used, and therefore the maximum rotation angle of the rotary valve type multi-way switching valve (100) body during defrost operation is also approximately 90°.

[0168] Furthermore, by using a stepping motor or a servo motor, for example, to rotate the main body of the rotary valve type multi-way switching valve (100), it becomes possible to control the angle arbitrarily.

[0169] The above-described configuration enables phase adjustment (switching of the heat medium transport direction in the internal flow path (13) in accordance with the phase of the magnetic field fluctuation) even during rotation of the magnetic field modulation unit (15) and the rotary valve type multi-way switching valve (100).

[0170] (Variation 5) The magnetic refrigeration apparatus (1) of this modification is different from the fourth modification in that a phase adjustment mechanism (200, 300) as shown in FIG. 27 or 28 is installed between the rotary magnetic circuit (magnetic field modulation unit (15)) and the rotary valve type multi-way switching valve (100).

[0171] The phase adjustment mechanism (200) shown in FIG. 27 includes four bevel gears (206a, 206b, 206c, 206d) (collectively referred to as a bevel gear group (206)) and two spur gears (208a, 208b) (collectively referred to as a spur gear group (208)) housed in a casing (201). The bevel gear group (206) is housed in the upper casing (202), and the spur gear group (208) is housed in the lower casing (203). An input shaft (204), one end of which is supported by the bevel gear group (206) (bevel gear (206a)), is provided to penetrate the ceiling of the upper casing (202). An output shaft (205), one end of which is supported by the spur gear group (208) (spur gear (208b)), is provided to penetrate the bottom of the lower casing (203). A connecting shaft (207) is supported at one end by the bevel gear group (206) (bevel gear (206b)) and at the other end by the spur gear group (208) (spur gear (208a)), and is provided penetrating the bottom of the upper casing (202) (the ceiling of the lower casing (203)).

[0172] The upper view of FIG. 27 shows a cross-sectional configuration of the phase adjustment mechanism (200) as viewed from the axial direction, and the lower view of FIG. 27 shows a cross-sectional configuration of the phase adjustment mechanism (200) as viewed from the radial direction.

[0173] The bevel gear group (206) performs phase adjustment (switching the heat medium transport direction in the internal flow path (13) in response to the phase of the magnetic field fluctuation). The spur gear group (208) changes the rotation direction of the output shaft (205), which is coaxial with the rotary shaft (102) of the rotary valve type multi-way selector valve (100), to the same direction as the input shaft (204), which is coaxial with the shaft (rotation mechanism (15c)) of the magnetic field modulation unit (15). Two bevel gears (206c, 206d) of the bevel gear group (206) are installed to be rotatable with respect to the input shaft (204). By rotating the two bevel gears (206c, 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, 213) of the bevel gears (206c, 206d) are supported by bearings (212, 214) provided on a support member (210) in the upper casing (202). When the rotation angle (hereinafter referred to as the phase adjustment angle) of the bevel gears (206c, 206d) is changed, a phase rotation angle twice the phase adjustment angle appears on the output shaft (205) in the direction opposite to the rotation direction of the bevel gears (306c, 306d). Controlling the phase adjustment angle using, for example, a stepping motor or a servo motor enables arbitrary angle control. The above-described configuration enables phase adjustment (switching the heat medium transport direction in the internal flow path (13) in response to the phase of the magnetic field fluctuation) even during rotation of the magnetic field modulation unit (15) and the rotary valve type multi-way selector valve (100). Furthermore, since the rotary valve type multi-way switching valve (100) body can remain fixed, there are no restrictions on piping or the like.

[0174] Note that the spur gear group (208) of the phase adjustment mechanism (200) shown in Fig. 27 may be replaced with bevel gears to form a phase adjustment mechanism (300) shown in Fig. 28. Note that Fig. 28 shows a cross-sectional configuration of the phase adjustment mechanism (300) as viewed from the radial direction.

[0175] The phase adjustment mechanism (300) includes a first bevel gear group (306) consisting of four bevel gears (306a, 306b, 306c, 306d) and a second bevel gear group (306) consisting of four bevel gears (307a, 307b, 307c, 307d) housed within a casing (301). The first bevel gear group (306) is housed in an upper space (302) of the casing (301), and the second bevel gear group (306) is housed in a lower space (303) of the casing (301). An input shaft (304), one end of which is supported by the first bevel gear group (306) (bevel gear (306a)), is provided penetrating the ceiling of the casing (301). An output shaft 305, one end of which is supported by the second bevel gear group 306 (bevel gear 307b), is provided to pass through the bottom of the casing 301. The bevel gear group 306b facing the bevel gear 306a in the first bevel gear group 306 and the bevel gear 307a facing the bevel gear 307b in the second bevel gear group 307 are integrally formed.

[0176] The first bevel gear group (306) performs phase adjustment (switching the heat medium transport direction in the internal flow path (13) in response to the phase of the magnetic field fluctuation). The second bevel gear group (306) changes the rotation direction of the output shaft (305) coaxial with the rotary shaft (102) of the rotary valve type multi-way selector valve (100) to the same direction as the input shaft (304) coaxial with the shaft (rotation mechanism (15c)) of the magnetic field modulation unit (15).

[0177] Two bevel gears (306c, 306d) of the first bevel gear group (306) are rotatably installed relative to the input shaft (304), and the phase difference (hereinafter referred to as the phase rotation angle) between the input shaft (304) and the output shaft (305) can be changed by rotating the two bevel gears (306c, 306d). The shafts (311, 313) of the bevel gears (306c, 306d) are supported by bearings (312, 314) provided on a support member in the upper space (302), respectively. When the rotation angle (hereinafter referred to as the phase adjustment angle) of the bevel gears (306c, 306d) is changed, a phase rotation angle twice the phase adjustment angle appears on the output shaft (305) in the direction opposite to the rotation direction of the bevel gears (306c, 306d). By using, for example, a stepping motor or a servo motor to control the phase adjustment angle, it becomes possible to control the angle arbitrarily.

[0178] Two bevel gears (307c, 307d) of the second bevel gear group (307) are installed to be rotatable about the output shaft (305). Shafts (321, 323) of the bevel gears (307c, 307d) are supported by bearings (322, 324) provided on the side walls of the casing (301), respectively.

[0179] The above-described configuration enables phase adjustment (switching the heat medium transport direction in the internal flow path (13) in response to the phase of the magnetic field fluctuation) even during rotation of the magnetic field modulation unit (15) and the rotary valve type multi-way switching valve (100). Furthermore, since the main body of the rotary valve type multi-way switching valve (100) can remain fixed, there are no restrictions on piping, etc. Furthermore, since the input shaft (304) and the output shaft (305) can be arranged coaxially, a phase adjustment mechanism (300) can be easily installed between the rotary magnetic circuit (magnetic field modulation unit (15)) and the rotary valve type multi-way switching valve (100).

[0180] (Variation 6) Fig. 29 is a piping diagram of a magnetic refrigeration device (1) according to Modification 6. In Fig. 29, the same components as those in the embodiment shown in Fig. 1 are denoted by the same reference numerals.

[0181] In the magnetic refrigeration apparatus (1) of the sixth modified example, as shown in FIG. 29, a first fan (16f) is disposed near the first heat exchanger (16). The first fan (16f) is driven by a first motor (16m). A second fan (17f) is disposed 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).

[0182] A feature of this modification is that, in the defrosting operation of the above-described embodiment, the operation of the fans (16f, 17f) is controlled as described below.

[0183] In the first fan control, when the temperature of the second heat exchanger (17) is higher than the ambient temperature of the second heat exchanger (17), the second fan (17f) is stopped in the defrosting operation. In this way, by stopping the second fan (17f) 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, heat radiation from the outdoor heat exchanger to the outdoor air can be prevented, and defrosting can be performed efficiently.

[0184] Alternatively, instead of or in addition to the first fan control, a second fan control, which will be described below, may be performed.

[0185] In the second fan control, the first heat exchanger (16) is an indoor heat exchanger, and the first fan (indoor fan) (16f) is stopped in the defrost operation, thereby preventing the indoor space temperature from decreasing due to the blowing of cold air from the indoor unit provided with the indoor heat exchanger.

[0186] (Other embodiments) In the above embodiments and modifications, a magnetic refrigeration device, which is a solid-state refrigeration device, has been illustrated, but the solid-state refrigeration device may use a method other than magnetic refrigeration that induces a magnetocaloric effect in the magnetic working material 12. In this disclosure, the solid refrigerant material also includes a material that has properties intermediate between a liquid and a solid, such as a flexible crystal.

[0187] Other types of solid-state refrigeration devices include, for example, 1) a system that induces an electrocaloric effect in a solid refrigerant material, 2) a system that induces a barocaloric effect in a solid refrigerant material, and 3) a system that induces an elastocaloric effect in a solid refrigerant material.

[0188] In the solid-state refrigeration device of type 1), the force field application unit (hereinafter also referred to as the inducing unit) applies an electric field fluctuation to the solid refrigerant material, which causes the solid refrigerant material to undergo a phase transition from ferroelectric to paraelectric, causing the solid refrigerant material to generate or absorb heat.

[0189] In the solid refrigeration device of type 2), the inducer applies pressure fluctuations to the solid refrigerant material, causing the solid refrigerant material to undergo a phase transition, generating or absorbing heat.

[0190] In the solid-state refrigeration device of type 3), the inducer applies stress fluctuations to the solid refrigerant material, causing the solid refrigerant material to undergo a phase transition, generating or absorbing heat.

[0191] Although the embodiments and modifications have been described above, it will be understood that various modifications in form and details are possible without departing from the spirit and scope of the claims. Furthermore, the above embodiments and modifications may be combined or substituted as appropriate. Furthermore, the terms "first," "second," etc., described above, are used to distinguish the terms to which these terms are attached, and do not limit the number or order of the terms. [Industrial Applicability]

[0192] As described above, the present disclosure is useful for solid-state refrigeration devices, particularly magnetic refrigeration devices. [Explanation of symbols]

[0193] 1. Magnetic refrigeration equipment (solid-state refrigeration equipment) 11 Storage section 11a to 11e Partial storage section 12 Magnetically active materials (solid refrigerant materials) 12a-12e Multiple substances with different temperatures at which the calorific effect is maximized 13 Internal flow path 15 Magnetic field modulation section (force field modulation section) 16 1st heat exchanger 16th floor No. 1 fan (indoor fan) 17 Second heat exchanger 17F 2nd Fan (Fan) 21 Reciprocating pump (heat medium transport section) 50 Heat medium transport section 100 Rotary valve type multi-way switching valve (heat medium transport section) C Heat carrier circuit

Claims

1. a storage section (11) having a solid refrigerant material (12) and an internal flow path (13) through which a heat transfer medium flows while exchanging heat with the solid refrigerant material (12); a force field modulation unit (15) that applies a force field fluctuation to the solid refrigerant material (12) in the storage unit (11) to induce a calorific effect; a first heat exchanger (16); a second heat exchanger (17); a heat medium circuit (C) connecting the first heat exchanger (16), the second heat exchanger (17), and the internal flow path (13); a heat medium transport unit (21, 50, 100) that transports the heat medium back and forth to the solid refrigerant material (12) in the storage unit (11) in response to the force field fluctuation in the heat medium circuit (C), A solid-state refrigeration system (1) that performs a heating operation in which the heat medium heated by the solid refrigerant material (12) is dissipated in the first heat exchanger (16) and the heat medium cooled by the solid refrigerant material (12) is absorbed in the second heat exchanger (17), and a defrosting operation in which frost adhering to the second heat exchanger (17) during the heating operation is removed, the solid refrigerant material (12) includes a plurality of materials (12a to 12e) each having a different temperature at which the calorific effect is maximized; the plurality of substances (12a to 12e) are arranged along the internal flow path (13) in order of decreasing temperature; In the defrosting operation, a transport direction of the heat medium in the internal flow path (13) relative to a phase of the force field fluctuation is switched to a direction opposite to that in the heating operation; the solid refrigerant material (12) is a magnetically working material (12); the force field modulation unit (15) is a magnetic field modulation unit (15) that applies a magnetic field fluctuation to the magnetic working material (12), The heat medium transfer section (21, 50, 100) is composed of a heat medium pump (21A) and a rotary valve type multi-way selector valve (100), a phase adjustment mechanism (200, 300) is provided between the magnetic field modulation unit (15) and the rotary valve type multi-way switching valve (100); The phase adjustment mechanism (200, 300) includes a first gear group (206, 306) that switches the transport direction of the heat medium in the internal flow path (13) in response to the phase of the magnetic field fluctuation, and a second gear group (208, 307) that changes the rotation direction of an output shaft (205, 305) that is coaxial with a rotation shaft (102) of the rotary valve type multi-way selector valve (100) to the same direction as an input shaft (204, 304) that is coaxial with a rotation mechanism (15c) of the magnetic field modulation unit (15). Solid refrigeration equipment.

2. 2. The solid-state refrigeration device of claim 1, the storage section (11) includes a plurality of partial storage sections (11a to 11e) connected in series to one another in the heat medium circuit (C), Each of the plurality of partial containers (11a to 11e) contains at least one substance among the plurality of substances (12a to 12e). Solid refrigeration equipment.

3. 2. The solid-state refrigeration device of claim 1, a fan (17f) for blowing 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 in the defrosting operation. Solid refrigeration equipment.

4. 2. The solid-state refrigeration device of claim 1, the first heat exchanger (16) is an indoor heat exchanger, an indoor fan (16f) that sends air to the indoor heat exchanger; The indoor fan (16f) is stopped during the defrosting operation. Solid refrigeration equipment.

5. 2. The solid-state refrigeration device of claim 1, the magnetic field modulation unit (15) performs a first modulation operation of applying a predetermined magnetic field to the magnetic working material (12) and a second modulation operation of applying a magnetic field smaller than the predetermined magnetic field to the magnetic working material (12) or removing the predetermined magnetic field; In a cycle in which the heat dissipation operation by the first modulation operation and the heat absorption operation by the second modulation operation are repeated, the frequency of the magnetic field fluctuation is increased during the defrost operation. Solid refrigeration equipment.

6. 2. The solid-state refrigeration device of claim 1, In the defrosting operation, the flow rate of the heat medium in the heat medium circuit (C) is increased. Solid refrigeration equipment.

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