EP2038590A1 - Rotation type regenerator and magnetic refrigerator using the regenerator - Google Patents

Rotation type regenerator and magnetic refrigerator using the regenerator

Info

Publication number
EP2038590A1
EP2038590A1 EP06812562A EP06812562A EP2038590A1 EP 2038590 A1 EP2038590 A1 EP 2038590A1 EP 06812562 A EP06812562 A EP 06812562A EP 06812562 A EP06812562 A EP 06812562A EP 2038590 A1 EP2038590 A1 EP 2038590A1
Authority
EP
European Patent Office
Prior art keywords
amr
magnet
hole
regenerator
transfer fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP06812562A
Other languages
German (de)
French (fr)
Other versions
EP2038590A4 (en
Inventor
Seung Hoon Shin
Dong Kwan Lee
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
WiniaDaewoo Co Ltd
Original Assignee
Daewoo Electronics Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daewoo Electronics Co Ltd filed Critical Daewoo Electronics Co Ltd
Publication of EP2038590A1 publication Critical patent/EP2038590A1/en
Publication of EP2038590A4 publication Critical patent/EP2038590A4/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B21/00—Machines, plants or systems, using electric or magnetic effects
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2321/00—Details of machines, plants or systems, using electric or magnetic effects
    • F25B2321/002—Details of machines, plants or systems, using electric or magnetic effects by using magneto-caloric effects
    • F25B2321/0022—Details of machines, plants or systems, using electric or magnetic effects by using magneto-caloric effects with a rotating or otherwise moving magnet
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]

Definitions

  • the present invention relates to a regenerator using a rotation type magnet member and an active magnetic regenerator (hereinafter referred to as "AMR"), and a magnetic refrigerator using the same.
  • AMR active magnetic regenerator
  • a temperature of a magnetic refrigerant material which has a magnetic field applied thereto as a magnet moves to a right increases from a dotted line to a solid line
  • the temperature of the magnetic refrigerant material drops from the dotted line to the solid line as a heat transfer fluid at a cold side moves to a hot side, and the heat transfer fluid is gradually heated to be hot at a right outlet, thereby emitting heat by an heat exchange with the hot side
  • the temperature of the magnetic refrigerant material which has a magnetic field erased as the magnet moves to a left decreases more from the dotted line to the solid line
  • the magnetic refrigerant material Due to the movement of the heat transfer fluid from the hot side to the cold side, the magnetic refrigerant material is heated from the temperature of the dotted line to that of the solid line, and the heat transfer fluid is relatively cooled to be cold at a left outlet, thereby absorbing heat from the cold side to cool the cold side.
  • a temperature of the heat transfer fluid heated in a first AMR bed 1OA in the magnetic field is dropped to an atmospheric temperature by a hot-side heat exchanger 70 and the heat transfer fluid is then passed through the second AMR bed 1OB.
  • a magnetic refrigerant material layer 16 has a low temperature, the temperature of the heat transfer fluid drops while passing through the magnetic refrigerant material layer 16.
  • the heat transfer fluid having the low temperature passes through a cold-side heat exchanger 60 and then enters the first AMR bed 1OA to be heated.
  • the heat transfer fluid then flows to the hot- side heat exchanger 70, the second AMR bed 1OB and the cold-side heat exchanger 60 to complete the one cycle.
  • a channel switch 30 reverses the flow of the heat transfer fluid to generate a reverse cycle.
  • an AMR bed 10 includes a container 12 of a cylinder type, a plurality of magnetic refrigerant material layers 16 stored inside the container 12, and meshes 14.
  • the container 12 includes heat transfer fluid inlet/outlet ports 18a and 18b, which may be connected to the heat exchange tube 32 or 34. Disclosure of Invention
  • a rotational regenerator comprising: a first AMR and a second AMR including a magnetocaloric material for passing through a flow of a heat transfer fluid; a magnet; and a magnet rotating assembly for applying or erasing a magnetic field by disposing the magnet at the first AMR or the second AMR, wherein each of the first AMR and the second AMR comprises an AMR bed disposed in a lengthwise direction of a through-hole being filled up with the magnetocaloric material, and cold-side and hot-side AMR nozzles coupled to the AMR bed and connected to the through-hole, and wherein one of the AMR nozzles includes a distribution chamber for uniformly distributing the heat transfer fluid to an entirety of a cross-section of the through-hole.
  • a magnetic refrigerator comprising: a first AMR and a second AMR including a magnetocaloric material for passing through a flow of a heat transfer fluid; a magnet; a magnetic rotating assembly for applying or erasing a magnetic field by disposing the magnet at the first AMR or the second AMR; and cold- side and hot-side heat exchangers thermally connected to the first AMR and the second AMR, wherein each of the first AMR and the second AMR comprises an AMR bed disposed in a lengthwise direction of a through-hole being filled up with the magnetocaloric material, and cold-side and hot-side AMR nozzles coupled to the AMR bed and connected to the through-hole, and wherein one of the AMR nozzles includes a distribution chamber for uniformly distributing the heat transfer fluid to an entirety of a cross-section of the through-hole.
  • the magnet rotating assembly comprises a body for supporting the magnet disposed upper and lower sides of the first AMR or the second AMR, a rotating plate for supporting the body, and a rotational power transfer member for transferring a rotational power to the rotating plate, and wherein each of the first AMR and the second AMR is supported in a horizontal direction perpendicular to a vertical tower.
  • the distribution chamber is connected to a first end of the AMR nozzle, and an inlet/outlet is formed at a second end thereof, and wherein the inlet/ outlet of the AMR nozzle is right-angled such that the inlet/outlet is on a same plane with the first AMR and the second AMR, thereby reducing a radius of a rotation by preventing an interference with the rotation of the magnet.
  • AMR nozzle a leakage of the magnetocaloric material and the heat transfer fluid is prevented.
  • the through-hole comprises an upper through-hole and a lower through-hole divided by a ribbed compartment, a distortion of the AMR bed due to a pressure of the heat transfer fluid is prevented.
  • regenerator and the magnetic refrigerator using the same in accordance with the present invention have following advantages.
  • the magnetic refrigerator since the magnetic refrigerator includes the distribution chamber having a size almost identical to that of the cross-section of the magnetocaloric material of the AMR bed, the heat transfer fluid flows uniformly throughout the magnetocaloric material, resulting in a suppression of the corrugation formed by partial flow thereof to improve the heat exchange efficiency.
  • the heat exchange efficiency is improved by employing the structure wherein the heat transfer fluid always passes through the magnetocaloric material.
  • an adiabatic state is achieved by employing the plastic AMR and by preventing an exposure of the magnetocaloric material to outside, resulting in the improvement of the heat exchange efficiency.
  • the through-hole of the AMR bed has the upper and the lower through-holes divided by the ribbed compartment, the distortion of a shape of the AMR due to the pressure of the heat transfer fluid is prevented. Even when the distortion occurs, the heat transfer fluid cannot bypass the magnetocaloric material due to the structure of the distribution chamber, resulting in the high heat exchange efficiency.
  • FIG. 1 is a schematic diagram a conventional active magnetic refrigerator.
  • FIG. 2 is a schematic diagram illustrating a configuration of a conventional active magnetic refrigerator.
  • FIG. 3 is a cross-sectional diagram illustrating an AMR bed of the conventional active magnetic refrigerator of Fig. 2.
  • FIG. 4 is a perspective view schematically illustrating a rotation type regenerator in accordance with a preferred embodiment of the present invention.
  • FIG. 5 is a perspective disassembled view illustrating a main portion of an AMR of
  • FIGs. 6 through 14 are diagrams illustrating a cycle of a magnetic refrigerator.
  • FIG. 4 is a perspective view schematically illustrating a rotation type regenerator in accordance with a preferred embodiment of the present invention
  • Fig. 5 is a perspective disassembled view illustrating a main portion of an AMR of Fig. 4
  • Figs. 6 through 14 are diagrams illustrating a cycle of a magnetic refrigerator.
  • a magnetic refrigerator in accordance with a preferred embodiment of the present invention comprises a regenerator 100, a cold- side heat exchanger 160 and a hot-side heat exchanger 170 thermally connected to the regenerator 100. While the cold-side heat exchanger 160 performs a cooling, the hot- side heat exchanger 170 performs a heat emission.
  • the regenerator 100 comprises an AMR 110, a magnet member 210 and a magnet rotating assembly for applying or erasing a magnetic field to the AMR 110.
  • the AMR 110 comprises a first AMR 11OA and a second AMR 11OB. As shown in
  • each of the AMR 110 comprises an AMR bed 111 including the magnetocaloric material for passing through a flow of the heat transfer fluid, a cold-side AMR nozzle connector 120L and a hot-side AMR nozzle connector 120L attached to both sides of the AMR bed the AMR bed 111.
  • a through-hole 114 to be filled up with the magnetocaloric material is formed in the
  • AMR bed 111 along a lengthwise direction thereof.
  • the cold-side AMR nozzle connector 120L and the hot-side AMR nozzle connector 120L are attached to the through-hole 114.
  • a cold-side inlet 121L and a cold-side distribution chamber 123L are disposed at each end of the cold-side AMR nozzle connector 120L, and a hot-side inlet 121H and a hot-side distribution chamber 123H are disposed at each end of the hot- side AMR nozzle connector 120H.
  • the distribution chambers 123L and 123H serve as a distribution chamber for uniform distribution through entire cross-section of a flow path of the through-hole 114.
  • a plurality of the first AMR 11OA are mounted at an opposing position, and a plurality of the second AMR 11OB are mounted between the first AMR 11OA, i.e. a cross structure.
  • the heat transfer fluid always passes through the magnetocaloric material, thereby improving the heat exchange efficiency.
  • the AMR beds 11 IA and 11 IB or the entire AMR bed 111 comprises a plastic.
  • the plastic has a large adiabatic effect and a wide temperature slope.
  • the through-hole 114 comprises an upper through-hole UP and a lower through-hole LP divided by a ribbed compartment R.
  • the ribbed compartment R serves a function of a rib such that the ribbed compartment R prevents a distortion of the AMR bed 111 due to a pressure.
  • a mesh M and plastic packing S are mounted at a mounting groove 115 of the through-hole 114 in order to prevent a leakage of the magnetocaloric material and the heat transfer fluid.
  • the cold-side heat exchanger 160 and the hot-side heat exchanger 170 are thermally coupled to the AMR 110 through heat exchange tubes 132, 133, 134, 135 and 136.
  • the flow of the heat transfer fluid is formed by a pump 140.
  • a change of a direction of the heat transfer fluid is carried out by solenoid valves SOLI through SOL4.
  • a bypass tube the bypass tube 137 is connected between an inlet and an outlet of the pump 140.
  • the magnet member 210 comprises the magnet 211 and a body 213 for supporting the magnet 211.
  • the magnet rotating assembly comprises a rotating plate 230 for supporting the magnet member 210 and a rotational power transfer member (not shown) for transferring a rotational power to the rotating plate 230.
  • the rotational power transfer member may be embodied various components such as a gear, a belt and a motor.
  • the AMR bed 111 is supported in a horizontal direction perpendicular to a vertical tower 150 such that the AMR bed 111 may move between the magnet 211.
  • the cold-side inlet 121L and the hot-side inlet 121H of the cold- side AMR nozzle connector 120L and the hot-side AMR nozzle connector 120L are right-angled toward a vertical tower 150 such that the cold-side inlet 121L and the hot- side inlet 12 IH lie on a same plane as the AMR bed 111. This is to prevent an interference of a rotation of the magnet member occurring due to a size of a nipple for flowing the heat transfer fluid into the magnetocaloric material which is larger than a distance between the magnets.
  • the magnet member 210 may be used in a small space when a radius of a rotation is minimized.
  • Fig. 6 illustrates a state wherein the two magnet members 210 are accurately positioned at the space between the first AMR 11OA and the second AMR 11OB. It is preferable that the magnet members 210 have an angle of 180 therebetween. Since the heat transfer fluid should not flow in the first AMR HOA and the second AMR HOB in Fig. 1, the solenoid valves SOLI through SOL4 are OFF, and the heat transfer fluid is bypassed through the solenoid valve SOL3 and the solenoid valve SOL4 coupled to the bypass tube 137.
  • the heat transfer fluid having the atmospheric temperature that has passed through the hot-side heat exchanger 170 is cooled by passing through the second AMR HOB via the heat exchange tube 132, and the heat transfer fluid is cooled additionally by passing through the opposing second AMR HOB, thereby providing a dual-cooling effect.
  • the temperature of the dual-cooled heat transfer fluid returns to the atmospheric temperature (actually, to a temperature a little lower than the atmospheric temperature) by passing through the cold-side heat exchanger 160 to be subjected to a first heating by passing through the first AMR 11OA and to a second heating by passing through the opposing first AMR 11OA.
  • the heat transfer fluid that has passed through the opposing first AMR 11OA is subjected to the dual-cooling and flows to the pump 140 through the heat exchange tube 134 and the heat exchange tube 135.
  • the heat transfer fluid passes through the pump 140 and the hot-side heat exchanger 170 to return to the atmospheric temperature (actually, to a temperature a little higher than the atmospheric temperature).
  • the heat transfer fluid is then enters the AMR HOB.
  • Fig. 8 illustrates a state after the plurality of the AMRs 11OA is in the magnet 211 completely and before the plurality of the AMRs 11OA move out of the magnet 211 while the heat transfer fluid flows in a direction described above.
  • the solenoid valve SOL2 is OFF and the solenoid valves SOLI, SOL3 and SOL4 are ON, wherein a cold-side inlet 121AL and a hot-side inlet 121AH of the AMR 11OA serve as a cold-side inlet and a hot-side outlet, a hot-side inlet 121BH and a cold-side inlet 121BL of the AMR 11OB serve as the hot-side outlet and the cold-side inlet.
  • the heat transfer fluid does not flow to the AMR 110 from a moment when the plurality of the AMR 11OA starts to move in order to move out of the magnet 211 but bypassed.
  • the heat transfer fluid pass through the pump 140 and the hot-side heat exchanger 170 to return to the atmospheric temperature (actually, to a temperature a little higher than the atmospheric temperature) to enter the plurality of the AMR 11OA via the heat exchange tube 134.
  • the above-described process forms a single cycle.
  • the solenoid valve SOLI is OFF and the solenoid valves SOL2, SOL3 and SOL4 are ON, wherein the cold-side inlet 121AL and the hot-side inlet 121AH of the AMR 11OA serve as a cold-side outlet and a hot-side inlet, a hot-side inlet 121BH and a cold-side inlet 121BL of the AMR HOB serve as the hot-side inlet and the cold-side outlet.
  • the heat transfer fluid does not flow to the AMR 110 from a moment when the plurality of the AMR HOB starts to move in order to move out of the magnet 211 but bypassed.
  • FIG. 6 through 14 illustrates a half cycle of a total rotational cycle, and the half cycle shown in Figs. 6 through 14 is repeated until the magnet member 210 returns to an initial position to complete the total rotational cycle.
  • An advantage of the cycle of the magnetic refrigerator in accordance with the preferred embodiment of the present invention lies in that the heat exchange efficiency is improved by employing a structure wherein the heat transfer fluid directly passes through the magnetocaloric material, and the four AMRs 110 are connected for more magnetocaloric material, resulting in double cooling effects.
  • the AMR includes the ribbed compartment which prevents the distortion of a shape of the AMR due to the pressure of the heat transfer fluid. Even when the distortion occurs, the heat transfer fluid cannot bypass the magnetocaloric material due to the structure of the distribution chamber, resulting in a high heat exchange efficiency.
  • the AMR 110 having a shape of a simple plate, the AMR 110 provides the high efficiency and is formed in plastic for an easy molding.
  • the magnetic refrigerator in accordance with the preferred embodiment of the present invention employs a rotational AMR cycle operation, the high cooling effect is provided due to a temperature slope of a low temperature and a high temperature.
  • the heat transfer fluid is dual-cooled by passing two AMRs, and dual-heated by passing two AMRs to provide twice the cooling efficiency.
  • the heat transfer fluid flows from the cold-side to the hot-side when AMR enters into the magnet, and the heat transfer fluid does not flow in the AMR when the AMR moves out of the magnet.
  • the heat transfer fluid flows from the hot- side to the cold- side when the AMR moves out of the magnet to be cooled.
  • the hot-side heat exchanger since the hot-side heat exchanger is disposed at the outlet of the pump, the hot-side heat exchanger cools the heat transfer fluid heated by the pump to the atmospheric temperature prior to entering the AMR.
  • the magnetocaloric material has a characteristic wherein the temperature thereof is changed when the magnetic field is applied.
  • the magnetocaloric material 112 comprises a gadolinium (Gd) of a fine powder type.
  • the gadolinium has pores having a high osmosis to the flow of the heat transfer fluid, and a superior absorption and emission of a heat.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Water Treatment By Electricity Or Magnetism (AREA)

Abstract

The present invention relates to a regenerator using a rotation type magnet member and an active magnetic regenerator, and a magnetic refrigerator using the same.

Description

Description
ROTATION TYPE REGENERATOR AND MAGNETIC REFRIGERATOR USING THE REGENERATOR
Technical Field
[1] The present invention relates to a regenerator using a rotation type magnet member and an active magnetic regenerator (hereinafter referred to as "AMR"), and a magnetic refrigerator using the same. Background Art
[2] A conventional active magnetic regenerator is disclosed in U.S. Patent No.
6,826,915. As shown in Fig. 1, (a) a temperature of a magnetic refrigerant material which has a magnetic field applied thereto as a magnet moves to a right increases from a dotted line to a solid line, (b) The temperature of the magnetic refrigerant material drops from the dotted line to the solid line as a heat transfer fluid at a cold side moves to a hot side, and the heat transfer fluid is gradually heated to be hot at a right outlet, thereby emitting heat by an heat exchange with the hot side, (c) The temperature of the magnetic refrigerant material which has a magnetic field erased as the magnet moves to a left decreases more from the dotted line to the solid line, (d) Due to the movement of the heat transfer fluid from the hot side to the cold side, the magnetic refrigerant material is heated from the temperature of the dotted line to that of the solid line, and the heat transfer fluid is relatively cooled to be cold at a left outlet, thereby absorbing heat from the cold side to cool the cold side.
[3] As shown in Figs. 2 and 3, in accordance with the conventional active magnetic regenerator including the above-described cycle, a temperature of the heat transfer fluid heated in a first AMR bed 1OA in the magnetic field is dropped to an atmospheric temperature by a hot-side heat exchanger 70 and the heat transfer fluid is then passed through the second AMR bed 1OB. At the same time, since the second AMR bed 1OB is outside the magnetic field, a magnetic refrigerant material layer 16 has a low temperature, the temperature of the heat transfer fluid drops while passing through the magnetic refrigerant material layer 16. The heat transfer fluid having the low temperature passes through a cold-side heat exchanger 60 and then enters the first AMR bed 1OA to be heated. The heat transfer fluid then flows to the hot- side heat exchanger 70, the second AMR bed 1OB and the cold-side heat exchanger 60 to complete the one cycle. Contrarily, when the second AMR bed 1OB is moved to a magnet circuit 22 by a movable mechanism 24, a channel switch 30 reverses the flow of the heat transfer fluid to generate a reverse cycle.
[4] On the other hand, as shown in Fig. 3, an AMR bed 10 includes a container 12 of a cylinder type, a plurality of magnetic refrigerant material layers 16 stored inside the container 12, and meshes 14. The container 12 includes heat transfer fluid inlet/outlet ports 18a and 18b, which may be connected to the heat exchange tube 32 or 34. Disclosure of Invention
Technical Problem
[5] However, the inlet/outlet ports 18a and 18b are installed at a center portion of the container 12. Therefore, the heat transfer fluid does not flow through an entire cross- section of the container 12, which renders the heat transfer fluid to flow through the magnetic refrigerant material 16 at the same spot, thereby making a smooth heat exchange difficult. Technical Solution
[6] It is an object of the present invention to provide a regenerator and a magnetic refrigerator using the same wherein a heat transfer fluid is dispersed and flown through an entire the magnetic refrigerant material to obtain a superior heat exchange characteristic.
[7] In order to achieve the above-described object, there is provided a rotational regenerator, comprising: a first AMR and a second AMR including a magnetocaloric material for passing through a flow of a heat transfer fluid; a magnet; and a magnet rotating assembly for applying or erasing a magnetic field by disposing the magnet at the first AMR or the second AMR, wherein each of the first AMR and the second AMR comprises an AMR bed disposed in a lengthwise direction of a through-hole being filled up with the magnetocaloric material, and cold-side and hot-side AMR nozzles coupled to the AMR bed and connected to the through-hole, and wherein one of the AMR nozzles includes a distribution chamber for uniformly distributing the heat transfer fluid to an entirety of a cross-section of the through-hole.
[8] There is also provided a magnetic refrigerator, comprising: a first AMR and a second AMR including a magnetocaloric material for passing through a flow of a heat transfer fluid; a magnet; a magnetic rotating assembly for applying or erasing a magnetic field by disposing the magnet at the first AMR or the second AMR; and cold- side and hot-side heat exchangers thermally connected to the first AMR and the second AMR, wherein each of the first AMR and the second AMR comprises an AMR bed disposed in a lengthwise direction of a through-hole being filled up with the magnetocaloric material, and cold-side and hot-side AMR nozzles coupled to the AMR bed and connected to the through-hole, and wherein one of the AMR nozzles includes a distribution chamber for uniformly distributing the heat transfer fluid to an entirety of a cross-section of the through-hole.
[9] It is preferable that the magnet rotating assembly comprises a body for supporting the magnet disposed upper and lower sides of the first AMR or the second AMR, a rotating plate for supporting the body, and a rotational power transfer member for transferring a rotational power to the rotating plate, and wherein each of the first AMR and the second AMR is supported in a horizontal direction perpendicular to a vertical tower.
[10] It preferable that the distribution chamber is connected to a first end of the AMR nozzle, and an inlet/outlet is formed at a second end thereof, and wherein the inlet/ outlet of the AMR nozzle is right-angled such that the inlet/outlet is on a same plane with the first AMR and the second AMR, thereby reducing a radius of a rotation by preventing an interference with the rotation of the magnet.
[11] In addition, when the AMRs include plastic, a wide temperature slope is obtained by an adiabatic state.
[12] Moreover, when a mesh and a packing are disposed between the AMR bed and the
AMR nozzle, a leakage of the magnetocaloric material and the heat transfer fluid is prevented.
[13] In addition, when the through-hole comprises an upper through-hole and a lower through-hole divided by a ribbed compartment, a distortion of the AMR bed due to a pressure of the heat transfer fluid is prevented.
Advantageous Effects
[14] As described above, the regenerator and the magnetic refrigerator using the same in accordance with the present invention have following advantages.
[15] As a first advantage, since the magnetic refrigerator includes the distribution chamber having a size almost identical to that of the cross-section of the magnetocaloric material of the AMR bed, the heat transfer fluid flows uniformly throughout the magnetocaloric material, resulting in a suppression of the corrugation formed by partial flow thereof to improve the heat exchange efficiency.
[16] As a second advantage, the heat exchange efficiency is improved by employing the rotational AMR cycle operation.
[17] As a third advantage, the heat exchange efficiency is improved by employing the structure wherein the heat transfer fluid always passes through the magnetocaloric material.
[18] As a fourth advantage, the leakage of the heat transfer fluid and the magnetocaloric material is prevented by using the mesh and the plastic packing.
[19] As a fifth advantage, the heat exchange efficiency is doubled using the four AMR.
[20] As a sixth advantage, an adiabatic state is achieved by employing the plastic AMR and by preventing an exposure of the magnetocaloric material to outside, resulting in the improvement of the heat exchange efficiency. [21] As a seventh advantage, since the through-hole of the AMR bed has the upper and the lower through-holes divided by the ribbed compartment, the distortion of a shape of the AMR due to the pressure of the heat transfer fluid is prevented. Even when the distortion occurs, the heat transfer fluid cannot bypass the magnetocaloric material due to the structure of the distribution chamber, resulting in the high heat exchange efficiency.
[22] As the eighth advantage, since the inlet/outlet of the AMR nozzle is right-angled to be on the same plane as the AMR such that the interference of the rotation of the magnet member occurring due to a size of a nipple for flowing the heat transfer fluid into the magnetocaloric material which is larger than a distance between the magnets is prevented and the radius of the rotation of is minimized to be used in the small space. Brief Description of the Drawings
[23] Fig. 1 is a schematic diagram a conventional active magnetic refrigerator.
[24] Fig. 2 is a schematic diagram illustrating a configuration of a conventional active magnetic refrigerator.
[25] Fig. 3 is a cross-sectional diagram illustrating an AMR bed of the conventional active magnetic refrigerator of Fig. 2.
[26] Fig. 4 is a perspective view schematically illustrating a rotation type regenerator in accordance with a preferred embodiment of the present invention.
[27] Fig. 5 is a perspective disassembled view illustrating a main portion of an AMR of
Fig. 4.
[28] Figs. 6 through 14 are diagrams illustrating a cycle of a magnetic refrigerator.
[29] [Description of reference numerals]
[30] 40,140: pump
[31] 60,160: cold-side heat exchangers
[32] 70,170: hot-side heat exchangers
[33] 100: regenerator
[34] 110 (11OA, HOB): AMR
[35] 111: AMR bed
[36] 114: through-hole
[37] 115: mounting groove
[38] 120L: cold-side AMR nozzle connector
[39] 120H: hot-side AMR nozzle connector
[40] 121L: cold-side inlet
[41] 121H: hot-side inlet
[42] 123L: cold-side distribution chamber
[43] 123H: hot-side distribution chamber [44] 150: tower
[45] 210: magnet member
[46] 211: magnet
[47] 213: body
[48] 230: rotating plate
[49] M: mesh
[50] R: ribbed compartment
[51] S: packing
[52] SOLI - SOL4: solenoid valves
Best Mode for Carrying Out the Invention
[53] The above-described objects and other objects and characteristics and advantages of the present invention will now be described in detail with reference to the accompanied drawings.
[54] Fig. 4 is a perspective view schematically illustrating a rotation type regenerator in accordance with a preferred embodiment of the present invention, Fig. 5 is a perspective disassembled view illustrating a main portion of an AMR of Fig. 4, and Figs. 6 through 14 are diagrams illustrating a cycle of a magnetic refrigerator.
[55] As shown in Figs. 4 through 14, a magnetic refrigerator in accordance with a preferred embodiment of the present invention comprises a regenerator 100, a cold- side heat exchanger 160 and a hot-side heat exchanger 170 thermally connected to the regenerator 100. While the cold-side heat exchanger 160 performs a cooling, the hot- side heat exchanger 170 performs a heat emission.
[56] As shown in Figs 4 and 5, the regenerator 100 comprises an AMR 110, a magnet member 210 and a magnet rotating assembly for applying or erasing a magnetic field to the AMR 110.
[57] The AMR 110 comprises a first AMR 11OA and a second AMR 11OB. As shown in
Fig. 5, each of the AMR 110 comprises an AMR bed 111 including the magnetocaloric material for passing through a flow of the heat transfer fluid, a cold-side AMR nozzle connector 120L and a hot-side AMR nozzle connector 120L attached to both sides of the AMR bed the AMR bed 111.
[58] A through-hole 114 to be filled up with the magnetocaloric material is formed in the
AMR bed 111 along a lengthwise direction thereof. In addition, the cold-side AMR nozzle connector 120L and the hot-side AMR nozzle connector 120L are attached to the through-hole 114.
[59] In addition, a cold-side inlet 121L and a cold-side distribution chamber 123L are disposed at each end of the cold-side AMR nozzle connector 120L, and a hot-side inlet 121H and a hot-side distribution chamber 123H are disposed at each end of the hot- side AMR nozzle connector 120H. The distribution chambers 123L and 123H serve as a distribution chamber for uniform distribution through entire cross-section of a flow path of the through-hole 114. Therefore, a partial contact with the magnetocaloric material and a corrugated shape is minimized to improve the heat exchange efficiency since the heat transfer fluid proceeds at the cold-side inlet 121L or the hot-side inlet 12 IH at a sufficient velocity to be diffused at the distribution chambers 123L and 123H, thereby flowing through the entire the through-hole 114. In addition, the cold- side inlet 12 IL and the hot-side inlet 12 IH are connected to heat exchange tubes 132 and 134.
[60] A plurality of the first AMR 11OA are mounted at an opposing position, and a plurality of the second AMR 11OB are mounted between the first AMR 11OA, i.e. a cross structure.
[61] Due to the cross structure, when an AMR bed 11 IA is in a magnet 211, an AMR bed 11 IB is position outside the magnet 211. A reason that a space exists between the AMR bed 11 IA and the AMR bed 11 IB is that the heat transfer fluid should not flow when the AMR bed 111 is outside the magnetic field. That is, the AMR bed 11 IB is cooled when the AMR bed 11 IA is heated.
[62] Due to an above-described structure of the AMR 110, the heat transfer fluid always passes through the magnetocaloric material, thereby improving the heat exchange efficiency.
[63] In addition, it is preferable that the AMR beds 11 IA and 11 IB or the entire AMR bed 111 comprises a plastic. The plastic has a large adiabatic effect and a wide temperature slope.
[64] On the other hand, the through-hole 114 comprises an upper through-hole UP and a lower through-hole LP divided by a ribbed compartment R. The ribbed compartment R serves a function of a rib such that the ribbed compartment R prevents a distortion of the AMR bed 111 due to a pressure.
[65] It is preferable that a mesh M and plastic packing S are mounted at a mounting groove 115 of the through-hole 114 in order to prevent a leakage of the magnetocaloric material and the heat transfer fluid.
[66] The cold-side heat exchanger 160 and the hot-side heat exchanger 170 are thermally coupled to the AMR 110 through heat exchange tubes 132, 133, 134, 135 and 136. The flow of the heat transfer fluid is formed by a pump 140. In addition, a change of a direction of the heat transfer fluid is carried out by solenoid valves SOLI through SOL4. Moreover, a bypass tube the bypass tube 137 is connected between an inlet and an outlet of the pump 140.
[67] The magnet member 210 comprises the magnet 211 and a body 213 for supporting the magnet 211. [68] The magnet rotating assembly comprises a rotating plate 230 for supporting the magnet member 210 and a rotational power transfer member (not shown) for transferring a rotational power to the rotating plate 230. The rotational power transfer member may be embodied various components such as a gear, a belt and a motor.
[69] It is preferable that the AMR bed 111 is supported in a horizontal direction perpendicular to a vertical tower 150 such that the AMR bed 111 may move between the magnet 211.
[70] It is preferable that the cold-side inlet 121L and the hot-side inlet 121H of the cold- side AMR nozzle connector 120L and the hot-side AMR nozzle connector 120L are right-angled toward a vertical tower 150 such that the cold-side inlet 121L and the hot- side inlet 12 IH lie on a same plane as the AMR bed 111. This is to prevent an interference of a rotation of the magnet member occurring due to a size of a nipple for flowing the heat transfer fluid into the magnetocaloric material which is larger than a distance between the magnets. In addition, the magnet member 210 may be used in a small space when a radius of a rotation is minimized.
[71] The cyclic operation of the magnetic refrigerator in accordance with the preferred embodiment of the present invention will now be described with reference to Figs. 6 through 14. It should be noted that the solenoid valves shown in Figs. 6 through 14 switches in a manner that the solenoid valves operates as an elbow type when OFF and as a straight type when ON.
[72] Fig. 6 illustrates a state wherein the two magnet members 210 are accurately positioned at the space between the first AMR 11OA and the second AMR 11OB. It is preferable that the magnet members 210 have an angle of 180 therebetween. Since the heat transfer fluid should not flow in the first AMR HOA and the second AMR HOB in Fig. 1, the solenoid valves SOLI through SOL4 are OFF, and the heat transfer fluid is bypassed through the solenoid valve SOL3 and the solenoid valve SOL4 coupled to the bypass tube 137.
[73] As shown Figs. 7 and 8, while a plurality of the first AMRs 11OA are in the magnet
211, a plurality of the second AMRs HOB are completely out of the magnet 211. Therefore, the heat transfer fluid having the atmospheric temperature that has passed through the hot-side heat exchanger 170 is cooled by passing through the second AMR HOB via the heat exchange tube 132, and the heat transfer fluid is cooled additionally by passing through the opposing second AMR HOB, thereby providing a dual-cooling effect. The temperature of the dual-cooled heat transfer fluid returns to the atmospheric temperature (actually, to a temperature a little lower than the atmospheric temperature) by passing through the cold-side heat exchanger 160 to be subjected to a first heating by passing through the first AMR 11OA and to a second heating by passing through the opposing first AMR 11OA. The heat transfer fluid that has passed through the opposing first AMR 11OA is subjected to the dual-cooling and flows to the pump 140 through the heat exchange tube 134 and the heat exchange tube 135. The heat transfer fluid passes through the pump 140 and the hot-side heat exchanger 170 to return to the atmospheric temperature (actually, to a temperature a little higher than the atmospheric temperature). The heat transfer fluid is then enters the AMR HOB. The above- described process forms a single cycle. Fig. 8 illustrates a state after the plurality of the AMRs 11OA is in the magnet 211 completely and before the plurality of the AMRs 11OA move out of the magnet 211 while the heat transfer fluid flows in a direction described above. At this time, the solenoid valve SOL2 is OFF and the solenoid valves SOLI, SOL3 and SOL4 are ON, wherein a cold-side inlet 121AL and a hot-side inlet 121AH of the AMR 11OA serve as a cold-side inlet and a hot-side outlet, a hot-side inlet 121BH and a cold-side inlet 121BL of the AMR 11OB serve as the hot-side outlet and the cold-side inlet.
[74] As shown Figs. 9 and 10, the heat transfer fluid does not flow to the AMR 110 from a moment when the plurality of the AMR 11OA starts to move in order to move out of the magnet 211 but bypassed.
[75] As shown Figs. 11 and 12, contrary to the cycle show in Figs. 7 and 8, while the plurality of the AMRs HOB are in the magnet 211, the plurality of the AMRs 11OA are completely out of the magnet 211. Therefore, the heat transfer fluid having the atmospheric temperature that has passed through the hot-side heat exchanger 170 is subjected to the dual-cooling by passing through the opposing AMR 11OA and the AMR 11OA via the heat exchange tube 134, and the heat transfer fluid returns to the atmospheric temperature (actually, to a temperature a little lower than the atmospheric temperature) by passing through the cold-side heat exchanger 160 to be subjected to the dual-heating by passing through the opposing AMR HOB and the AMR HOB and flows to the pump 140 through the heat exchange tube 132 and the heat exchange tube 133. The heat transfer fluid pass through the pump 140 and the hot-side heat exchanger 170 to return to the atmospheric temperature (actually, to a temperature a little higher than the atmospheric temperature) to enter the plurality of the AMR 11OA via the heat exchange tube 134. The above-described process forms a single cycle. At this time, the solenoid valve SOLI is OFF and the solenoid valves SOL2, SOL3 and SOL4 are ON, wherein the cold-side inlet 121AL and the hot-side inlet 121AH of the AMR 11OA serve as a cold-side outlet and a hot-side inlet, a hot-side inlet 121BH and a cold-side inlet 121BL of the AMR HOB serve as the hot-side inlet and the cold-side outlet.
[76] As shown Figs. 13 and 14, the heat transfer fluid does not flow to the AMR 110 from a moment when the plurality of the AMR HOB starts to move in order to move out of the magnet 211 but bypassed.
[77] Nine steps of Figs. 6 through 14 illustrates a half cycle of a total rotational cycle, and the half cycle shown in Figs. 6 through 14 is repeated until the magnet member 210 returns to an initial position to complete the total rotational cycle.
[78] An advantage of the cycle of the magnetic refrigerator in accordance with the preferred embodiment of the present invention lies in that the heat exchange efficiency is improved by employing a structure wherein the heat transfer fluid directly passes through the magnetocaloric material, and the four AMRs 110 are connected for more magnetocaloric material, resulting in double cooling effects. In addition, the AMR includes the ribbed compartment which prevents the distortion of a shape of the AMR due to the pressure of the heat transfer fluid. Even when the distortion occurs, the heat transfer fluid cannot bypass the magnetocaloric material due to the structure of the distribution chamber, resulting in a high heat exchange efficiency. Moreover, while the AMR 110 having a shape of a simple plate, the AMR 110 provides the high efficiency and is formed in plastic for an easy molding.
[79] In addition, since the magnetic refrigerator in accordance with the preferred embodiment of the present invention employs a rotational AMR cycle operation, the high cooling effect is provided due to a temperature slope of a low temperature and a high temperature. As described above, the heat transfer fluid is dual-cooled by passing two AMRs, and dual-heated by passing two AMRs to provide twice the cooling efficiency.
[80] Moreover, in accordance with a basic characteristic of the cycle, the heat transfer fluid flows from the cold-side to the hot-side when AMR enters into the magnet, and the heat transfer fluid does not flow in the AMR when the AMR moves out of the magnet. The heat transfer fluid flows from the hot- side to the cold- side when the AMR moves out of the magnet to be cooled.
[81] In addition, since the hot-side heat exchanger is disposed at the outlet of the pump, the hot-side heat exchanger cools the heat transfer fluid heated by the pump to the atmospheric temperature prior to entering the AMR.
[82] Moreover, the magnetocaloric material has a characteristic wherein the temperature thereof is changed when the magnetic field is applied. The magnetocaloric material 112 comprises a gadolinium (Gd) of a fine powder type. The gadolinium has pores having a high osmosis to the flow of the heat transfer fluid, and a superior absorption and emission of a heat.
[83] While the present invention has been particularly shown and described with reference to the preferred embodiment thereof, it will be understood by those skilled in the art that various changes in form and details may be effected therein without departing from the spirit and scope of the invention as defined by the appended claims Industrial Applicability [84] In accordance to present invention, a regenerator and a magnetic refrigerator using the same wherein a heat transfer fluid is dispersed and flown through an entire the magnetic refrigerant material to obtain a superior heat exchange characteristic can be provided.

Claims

Claims
[1] A rotational regenerator, comprising: a first AMR and a second AMR including a magnetocaloric material for passing through a flow of a heat transfer fluid; a magnet; and a magnet rotating assembly for applying or erasing a magnetic field to the magnetocaloric material by disposing the magnet at the first AMR or the second AMR, wherein each of the first AMR and the second AMR comprises an AMR bed disposed in a lengthwise direction of a through-hole being filled up with the magnetocaloric material, and cold-side and hot-side AMR nozzles coupled to the AMR bed and connected to the through-hole, and wherein at least one of the AMR nozzles includes a distribution chamber for uniformly distributing the heat transfer fluid to an entirety of a cross-section of the through-hole.
[2] The rotational regenerator in accordance with claim 1, wherein the magnet rotating assembly comprises a body for supporting the magnet disposed upper and lower sides of the first AMR or the second AMR, a rotating plate for supporting the body, and a rotational power transfer member for transferring a rotational power to the rotating plate, and wherein each of the first AMR and the second AMR is supported in a horizontal direction perpendicular to a vertical tower.
[3] The rotational regenerator in accordance with claim 2, wherein the distribution chamber is connected to a first end of the AMR nozzle, and an inlet/outlet is formed at a second end thereof, and wherein the inlet/outlet of the AMR nozzle is right-angled such that the inlet/outlet is on a same plane with the first AMR and the second AMR.
[4] The rotational regenerator in accordance with one of claims 1 through 3, wherein the first AMR and the second AMR include plastic, respectively.
[5] The rotational regenerator in accordance with claim 4, wherein the through-hole comprises an upper through-hole and a lower through-hole divided by a ribbed compartment.
[6] The rotational regenerator in accordance with claim 5, wherein a mesh and a packing are disposed between the AMR bed and the AMR nozzle.
[7] A magnetic refrigerator, comprising: a first AMR and a second AMR including a magnetocaloric material for passing through a flow of a heat transfer fluid; a magnet; a magnetic rotating assembly for applying or erasing a magnetic field to the mag- netocaloric material by disposing the magnet at the first AMR or the second
AMR; and cold-side and hot-side heat exchangers thermally connected to the first AMR and the second AMR, wherein each of the first AMR and the second AMR comprises an AMR bed disposed in a lengthwise direction of a through-hole being filled up with the magnetocaloric material, and cold-side and hot-side AMR nozzles coupled to the
AMR bed and connected to the through-hole, and wherein one of the AMR nozzles includes a distribution chamber for uniformly distributing the heat transfer fluid to an entirety of a cross-section of the through-hole.
[8] The magnetic refrigerator in accordance with claim 7, wherein the magnet rotating assembly comprises a body for supporting the magnet disposed upper and lower sides of the first AMR or the second AMR, a rotating plate for supporting the body, and a rotational power transfer member for transferring a rotational power to the rotating plate, and wherein each of the first AMR and the second AMR is supported in a horizontal direction perpendicular to a vertical tower.
[9] The magnetic refrigerator in accordance with claim 8, wherein the distribution chamber is connected to a first end of the AMR nozzle, and an inlet/outlet is formed at a second end thereof, and wherein the inlet/outlet of the AMR nozzle is right-angled such that the inlet/outlet is on a same plane with the first AMR and the second AMR.
[10] The magnetic refrigerator in accordance with one of claims 7 through 9, wherein the first AMR and the second AMR include plastic, respectively, and wherein a mesh and a packing are disposed between the AMR bed and the AMR nozzle.
[11] The magnetic refrigerator in accordance with claim 10, wherein the through-hole comprises an upper through-hole and a lower through-hole divided by a ribbed compartment.
EP06812562.4A 2006-07-10 2006-11-13 Rotation type regenerator and magnetic refrigerator using the regenerator Withdrawn EP2038590A4 (en)

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KR1020060064344A KR100737781B1 (en) 2006-07-10 2006-07-10 Rotation type regenerator and magnetic refrigerator using the regenerator
PCT/KR2006/004729 WO2008007833A1 (en) 2006-07-10 2006-11-13 Rotation type regenerator and magnetic refrigerator using the regenerator

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EP2038590A1 true EP2038590A1 (en) 2009-03-25
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Families Citing this family (52)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101979937B (en) * 2010-10-15 2012-05-23 西安交通大学 Rotary magnetic refrigeration device and application thereof
WO2013012908A1 (en) * 2011-07-19 2013-01-24 Astronautics Corporation Of America System and method for reverse degradation of a magnetocaloric material
CN102305446A (en) * 2011-09-15 2012-01-04 芜湖博耐尔汽车电气系统有限公司 Magnetic refrigeration device for electric automobile air conditioner and control method for magnetic refrigeration device
US9709303B1 (en) 2011-11-30 2017-07-18 EMC IP Holding Company LLC Magneto-caloric cooling system
US9631842B1 (en) * 2011-11-30 2017-04-25 EMC IP Holding Company LLC Magneto-caloric cooling system
US20130186107A1 (en) * 2012-01-20 2013-07-25 Delta Electronics, Inc. Magnetic refrigeration control system, and method thereof
KR101866840B1 (en) * 2012-03-26 2018-06-14 삼성전자주식회사 Magnetic cooling apparatus
KR102158130B1 (en) * 2013-07-04 2020-09-21 삼성전자주식회사 Magnetic cooling apparatus
CN103925732B (en) * 2014-04-11 2016-05-04 佛山市川东磁电股份有限公司 A kind of rotary string utmost point magnetic refrigerating system
US9927155B2 (en) * 2014-09-15 2018-03-27 Astronautics Corporation Of America Magnetic refrigeration system with unequal blows
DE102015108954A1 (en) * 2015-06-08 2016-12-08 Eberspächer Climate Control Systems GmbH & Co. KG Temperature control unit, in particular Fahrzeugtemperiergerät
US10541070B2 (en) 2016-04-25 2020-01-21 Haier Us Appliance Solutions, Inc. Method for forming a bed of stabilized magneto-caloric material
US10299655B2 (en) 2016-05-16 2019-05-28 General Electric Company Caloric heat pump dishwasher appliance
US10047979B2 (en) 2016-07-19 2018-08-14 Haier Us Appliance Solutions, Inc. Linearly-actuated magnetocaloric heat pump
US10274231B2 (en) 2016-07-19 2019-04-30 Haier Us Appliance Solutions, Inc. Caloric heat pump system
US10047980B2 (en) 2016-07-19 2018-08-14 Haier Us Appliance Solutions, Inc. Linearly-actuated magnetocaloric heat pump
US10295227B2 (en) 2016-07-19 2019-05-21 Haier Us Appliance Solutions, Inc. Caloric heat pump system
US10281177B2 (en) 2016-07-19 2019-05-07 Haier Us Appliance Solutions, Inc. Caloric heat pump system
US10222101B2 (en) * 2016-07-19 2019-03-05 Haier Us Appliance Solutions, Inc. Linearly-actuated magnetocaloric heat pump
US10443585B2 (en) 2016-08-26 2019-10-15 Haier Us Appliance Solutions, Inc. Pump for a heat pump system
US10386096B2 (en) 2016-12-06 2019-08-20 Haier Us Appliance Solutions, Inc. Magnet assembly for a magneto-caloric heat pump
US10288326B2 (en) 2016-12-06 2019-05-14 Haier Us Appliance Solutions, Inc. Conduction heat pump
KR101893164B1 (en) * 2017-01-16 2018-08-30 엘지전자 주식회사 Magnetic cooling system
US11009282B2 (en) 2017-03-28 2021-05-18 Haier Us Appliance Solutions, Inc. Refrigerator appliance with a caloric heat pump
US10527325B2 (en) 2017-03-28 2020-01-07 Haier Us Appliance Solutions, Inc. Refrigerator appliance
US10451320B2 (en) 2017-05-25 2019-10-22 Haier Us Appliance Solutions, Inc. Refrigerator appliance with water condensing features
CN107270576A (en) * 2017-07-03 2017-10-20 浙江磁石科技有限公司 A kind of heat-exchange system of magnetic refrigerator
US10422555B2 (en) 2017-07-19 2019-09-24 Haier Us Appliance Solutions, Inc. Refrigerator appliance with a caloric heat pump
US10451322B2 (en) 2017-07-19 2019-10-22 Haier Us Appliance Solutions, Inc. Refrigerator appliance with a caloric heat pump
US10520229B2 (en) 2017-11-14 2019-12-31 Haier Us Appliance Solutions, Inc. Caloric heat pump for an appliance
US11022348B2 (en) 2017-12-12 2021-06-01 Haier Us Appliance Solutions, Inc. Caloric heat pump for an appliance
US10641539B2 (en) 2018-04-18 2020-05-05 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10648706B2 (en) 2018-04-18 2020-05-12 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with an axially pinned magneto-caloric cylinder
US10782051B2 (en) 2018-04-18 2020-09-22 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10551095B2 (en) 2018-04-18 2020-02-04 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10648704B2 (en) 2018-04-18 2020-05-12 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10648705B2 (en) 2018-04-18 2020-05-12 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly
US10557649B2 (en) 2018-04-18 2020-02-11 Haier Us Appliance Solutions, Inc. Variable temperature magneto-caloric thermal diode assembly
US10876770B2 (en) 2018-04-18 2020-12-29 Haier Us Appliance Solutions, Inc. Method for operating an elasto-caloric heat pump with variable pre-strain
US10830506B2 (en) 2018-04-18 2020-11-10 Haier Us Appliance Solutions, Inc. Variable speed magneto-caloric thermal diode assembly
US11015842B2 (en) 2018-05-10 2021-05-25 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with radial polarity alignment
US10989449B2 (en) 2018-05-10 2021-04-27 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with radial supports
US11054176B2 (en) 2018-05-10 2021-07-06 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with a modular magnet system
CN108895704B (en) * 2018-06-12 2020-08-18 西安交通大学 Variable load control system of rotary room temperature magnetic refrigerator and control method thereof
US11092364B2 (en) 2018-07-17 2021-08-17 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with a heat transfer fluid circuit
US10684044B2 (en) 2018-07-17 2020-06-16 Haier Us Appliance Solutions, Inc. Magneto-caloric thermal diode assembly with a rotating heat exchanger
US11274860B2 (en) 2019-01-08 2022-03-15 Haier Us Appliance Solutions, Inc. Mechano-caloric stage with inner and outer sleeves
US11193697B2 (en) 2019-01-08 2021-12-07 Haier Us Appliance Solutions, Inc. Fan speed control method for caloric heat pump systems
US11149994B2 (en) 2019-01-08 2021-10-19 Haier Us Appliance Solutions, Inc. Uneven flow valve for a caloric regenerator
US11168926B2 (en) 2019-01-08 2021-11-09 Haier Us Appliance Solutions, Inc. Leveraged mechano-caloric heat pump
US11112146B2 (en) 2019-02-12 2021-09-07 Haier Us Appliance Solutions, Inc. Heat pump and cascaded caloric regenerator assembly
US11015843B2 (en) 2019-05-29 2021-05-25 Haier Us Appliance Solutions, Inc. Caloric heat pump hydraulic system

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125861A (en) * 1964-03-24 Method and apparatus for heat transfer
US4507927A (en) * 1983-05-26 1985-04-02 The United States Of America As Represented By The United States Department Of Energy Low-temperature magnetic refrigerator
JPH10185339A (en) * 1996-10-30 1998-07-14 Toshiba Corp Cryogenic cold storage material, refrigerating machine employing the same and heat shielding material
WO2004059221A1 (en) * 2002-12-24 2004-07-15 Ecole D'ingenieurs Du Canton De Vaud Method and device for continuous generation of cold and heat by means of the magneto-calorific effect
EP1463068A2 (en) * 2003-03-28 2004-09-29 Kabushiki Kaisha Toshiba Magnetic composite material and method for producing the same

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2517415A1 (en) * 1981-11-27 1983-06-03 Commissariat Energie Atomique METHOD FOR REFRIGERATING OR HEAT PUMPING AND DEVICE FOR CARRYING OUT SAID METHOD
US4408463A (en) 1982-01-20 1983-10-11 Barclay John A Wheel-type magnetic refrigerator
DE3539584C1 (en) * 1985-11-08 1986-12-18 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5300 Bonn Device for magnetocaloric cold production
US4727722A (en) 1987-02-11 1988-03-01 The United States Of America As Represented By The United States Department Of Energy Rotary magnetic heat pump
JPH0224514A (en) * 1988-07-14 1990-01-26 Fanuc Ltd Optical encoder using optical fiber
JPH0370944A (en) * 1989-08-08 1991-03-26 Matsushita Electric Ind Co Ltd Air conditioner using magnetic refrigerator
US5249424A (en) * 1992-06-05 1993-10-05 Astronautics Corporation Of America Active magnetic regenerator method and apparatus
US5444983A (en) * 1994-02-28 1995-08-29 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Magnetic heat pump flow director
JPH10339591A (en) * 1997-06-10 1998-12-22 Komatsu Ltd Temperature controller utilizing heat pipe
JPH11132708A (en) * 1997-11-04 1999-05-21 Toyota Motor Corp Rotation angle sensor
US5934078A (en) * 1998-02-03 1999-08-10 Astronautics Corporation Of America Reciprocating active magnetic regenerator refrigeration apparatus
WO1999046544A1 (en) * 1998-03-13 1999-09-16 Hitachi, Ltd. Coolant distributor, and air conditioner using it
JP2003532861A (en) 2000-05-05 2003-11-05 ユニヴァーシティ オブ ヴィクトリア イノヴェーション アンド デヴェロップメント コーポレイション Apparatus and method for cooling and liquefying a fluid using magnetic refrigeration
JP4879449B2 (en) 2000-08-09 2012-02-22 アストロノーティックス コーポレイション オブ アメリカ Rotating bed type magnetic refrigerator
JP4303879B2 (en) * 2000-10-02 2009-07-29 株式会社東芝 Magnetic refrigeration equipment
JP2002195683A (en) * 2000-12-20 2002-07-10 Denso Corp Magnetic temperature regulating apparatus
JP2002228286A (en) * 2001-02-02 2002-08-14 Sumitomo Heavy Ind Ltd Cold storage tank
JP4622179B2 (en) * 2001-07-16 2011-02-02 日立金属株式会社 Magnetic refrigeration work substance, regenerative heat exchanger and magnetic refrigeration equipment
EP1454098B1 (en) 2001-12-12 2007-09-12 Astronautics Corporation Of America Rotating magnet magnetic refrigerator
JP4089281B2 (en) * 2002-04-26 2008-05-28 日立金属株式会社 Magnetic refrigeration work substance, regenerative heat exchanger and magnetic refrigeration equipment
JP2005205951A (en) * 2004-01-20 2005-08-04 Nissan Motor Co Ltd Connecting structure of air duct
JP4764647B2 (en) * 2004-03-09 2011-09-07 昭和電工株式会社 Flat plate manufacturing plate, flat tube, heat exchanger, and heat exchanger manufacturing method
JP4231022B2 (en) * 2005-03-31 2009-02-25 株式会社東芝 Magnetic refrigerator

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125861A (en) * 1964-03-24 Method and apparatus for heat transfer
US4507927A (en) * 1983-05-26 1985-04-02 The United States Of America As Represented By The United States Department Of Energy Low-temperature magnetic refrigerator
JPH10185339A (en) * 1996-10-30 1998-07-14 Toshiba Corp Cryogenic cold storage material, refrigerating machine employing the same and heat shielding material
WO2004059221A1 (en) * 2002-12-24 2004-07-15 Ecole D'ingenieurs Du Canton De Vaud Method and device for continuous generation of cold and heat by means of the magneto-calorific effect
EP1463068A2 (en) * 2003-03-28 2004-09-29 Kabushiki Kaisha Toshiba Magnetic composite material and method for producing the same

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2008007833A1 *

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KR100737781B1 (en) 2007-07-10
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US20090266083A1 (en) 2009-10-29
CN101523132A (en) 2009-09-02

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