CN116379637A - Double-regenerative low-temperature magnetic refrigeration device - Google Patents
Double-regenerative low-temperature magnetic refrigeration device Download PDFInfo
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- CN116379637A CN116379637A CN202310314630.5A CN202310314630A CN116379637A CN 116379637 A CN116379637 A CN 116379637A CN 202310314630 A CN202310314630 A CN 202310314630A CN 116379637 A CN116379637 A CN 116379637A
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 61
- 239000012530 fluid Substances 0.000 claims abstract description 44
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- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 claims abstract description 33
- 230000001172 regenerating effect Effects 0.000 claims abstract description 26
- 239000000463 material Substances 0.000 claims description 27
- 230000009977 dual effect Effects 0.000 claims description 17
- 230000001105 regulatory effect Effects 0.000 claims description 11
- 230000001276 controlling effect Effects 0.000 claims description 6
- 229910052757 nitrogen Inorganic materials 0.000 claims description 6
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- 239000007788 liquid Substances 0.000 abstract description 33
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- 238000005516 engineering process Methods 0.000 description 8
- 230000008929 regeneration Effects 0.000 description 7
- 238000011069 regeneration method Methods 0.000 description 7
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- 101100457021 Caenorhabditis elegans mag-1 gene Proteins 0.000 description 2
- 101100067996 Mus musculus Gbp1 gene Proteins 0.000 description 2
- 238000007664 blowing Methods 0.000 description 2
- 239000000945 filler Substances 0.000 description 2
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- 229910052734 helium Inorganic materials 0.000 description 2
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 description 2
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- 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
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- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
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- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- 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
- F25B49/00—Arrangement or mounting of control or safety devices
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- 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]
Abstract
The invention discloses a double-regenerative low-temperature magnetic refrigeration device, which comprises a plurality of active magnetic regenerators, a plurality of regenerators, a piston, a high-temperature heat exchanger and a low-temperature heat exchanger, and solves the technical problems that the existing liquid hydrogen temperature zone magnetic refrigeration device still has single flow path system, large regenerative loss, serious heat leakage, huge and compact whole structure, axial heat conduction of heat exchange fluid in a hydraulic piston and the like, and has the following beneficial effects: compared with the existing liquid hydrogen temperature zone magnetic refrigerating device, the right multi-stage heat regenerator and the left multi-stage active magnetic heat regenerator in the device are symmetrically arranged, in addition, the right multi-stage heat regenerator and two shunt branches are additionally arranged on the basis of only the multi-stage active magnetic heat regenerator, so that the heat regenerating performance of the liquid hydrogen temperature zone magnetic refrigerating device is improved, the flow path design is more reasonable, and the cooling performance of the liquid hydrogen temperature zone magnetic refrigerating device can be improved under the optimal flow working condition when the left multi-stage active magnetic heat regenerator works.
Description
Technical Field
The invention belongs to the technical field of refrigeration and low temperature, and particularly relates to a double-regenerative low-temperature magnetic refrigeration device.
Background
The hydrogen energy is a green clean energy source which is widely accepted and can be continuously developed, and the transportation and the storage of the hydrogen energy can be in the form of liquid hydrogen with larger energy storage density. The generation of liquid hydrogen needs the support of refrigeration and warm refrigeration technology, so the development of a liquid hydrogen temperature zone refrigeration system has important significance for the liquefaction and use of hydrogen energy.
The magnetic refrigeration is a refrigeration technology with wide application temperature range, mainly adopts the adiabatic demagnetization principle to refrigerate in the extremely low temperature range, and can easily obtain the refrigeration temperature below 1K. However, due to the limitation of the magnetocaloric effect of the magnetocaloric material, the magnetic refrigeration technology based on the adiabatic demagnetization principle has smaller achievable refrigeration temperature span in other refrigeration temperature areas. Therefore, in a room temperature area and a low temperature area, the magnetic refrigeration technology mainly carries out refrigeration based on active magnetic regenerative cycle so as to achieve a larger refrigeration temperature span.
The magnetocaloric effect is an inherent property of a magnetocaloric material, and refers to a physical phenomenon that the magnetic order of the magnetocaloric material changes in a changing magnetic field, so that the magnetic entropy of the magnetocaloric material changes, and the temperature of the magnetocaloric material rises or falls. An active magnetic regenerative cycle is a regenerative cycle that can increase the refrigeration temperature span of a magnetic refrigeration technology, often in combination with an inverse brayton cycle, further increasing the refrigeration temperature span of the magnetic refrigeration technology. It generally comprises four processes: adiabatic excitation process, hot blowing process, adiabatic demagnetizing process, and cold blowing process.
The Curie temperature is the critical temperature when the magnetocaloric material finds phase transition under the action of a magnetic field, and under a certain magnetic field, the magnetocaloric material obtains the maximum magnetic entropy change value and the maximum specific heat capacity value at the Curie temperature, namely the Curie temperature point is the peak point of the magnetic entropy change and the specific heat capacity of the magnetocaloric material. Research shows that the magnetocaloric material can exert its refrigerating potential more easily near the Curie temperature and has excellent refrigerating effect. Therefore, when the magnetic refrigeration has a wider temperature range, multi-layer or multi-stage magnetic refrigeration systems are mostly adopted to ensure that the magnetocaloric material can work near the Curie temperature of the magnetocaloric material, and the refrigeration performance of the magnetocaloric material can be better exerted.
In the liquid hydrogen temperature region, the magnetic refrigeration technology mainly involves the liquefaction of hydrogen, so that the refrigeration temperature range is generally large, such as from liquid nitrogen temperature to liquid hydrogen temperature. Therefore, the liquid hydrogen temperature zone magnetic refrigeration technology is mostly constructed by adopting a multi-stage active magnetic heat regenerator. However, because the liquid hydrogen temperature region involves low-temperature heat insulation, compared with other temperature regions, the flow path system is more complex, and the whole system is more difficult to optimize.
In the related art, in a liquid hydrogen temperature area, partial magnetic refrigeration devices are developed, but the problems of large regenerative loss, small refrigeration temperature span, serious heat leakage, non-compact whole structure and the like still exist. Therefore, in the liquid hydrogen temperature region, it is necessary to construct a double-regenerative low-temperature magnetic refrigeration device with higher refrigeration efficiency.
Disclosure of Invention
In order to solve at least one of the problems mentioned in the background art, an object of the present invention is to provide a dual regenerative low temperature magnetic refrigeration device.
The invention is realized by the following technical scheme:
a dual regenerative cryogenic magnetic refrigeration device comprising: the plurality of active magnetic heat regenerators are sequentially arranged from the first end to the second end, the magneto-thermal materials filled in each active magnetic heat regenerator are sequentially reduced, and each active magnetic heat regenerator is connected in series through a first pipeline;
the heat regenerators are sequentially arranged from the first end to the second end, the packing in each heat regenerator is sequentially reduced, each heat regenerator is connected in series through a second pipeline, and the heat regenerator at the second end is communicated with the active magnetic heat regenerator at the second end through a third pipeline;
the left cavity of the piston is communicated with the active magnetic heat regenerator at the first end through a fourth pipeline, and the right cavity is filled with heat exchange fluid and is communicated with the heat regenerator at the first end through a fifth pipeline;
the high-temperature heat exchanger is used for precooling the heat exchange fluid, one end of the high-temperature heat exchanger is communicated with the left cavity of the piston through a sixth pipeline, and the other end of the high-temperature heat exchanger is communicated with the active magnetic regenerator at the first end through a seventh pipeline;
the low-temperature heat exchanger is used for liquefying hydrogen to generate refrigeration, one end of the low-temperature heat exchanger is communicated with the active magnetic heat regenerator at the second end through an eighth pipeline, and the other end of the low-temperature heat exchanger is communicated with the heat regenerator at the second end through a ninth pipeline;
the flow direction of the third pipeline is from the heat regenerator to the active magnetic heat regenerator, the flow direction of the fourth pipeline is towards the first end, the flow direction of the seventh pipeline is towards the second end, and the flow direction of the eighth pipeline is from the low-temperature heat exchanger to the active magnetic heat regenerator.
In one embodiment, the number of the active magnetic regenerators is the same as the number of the regenerators, and the active magnetic regenerators and the regenerators are correspondingly arranged left and right so that the first pipelines and the second pipelines are mutually corresponding, each corresponding group of the first pipelines and the second pipelines are communicated through tenth pipelines, and each tenth pipeline is provided with a pressure regulating valve.
In one embodiment, the number of the active magnetic heat regenerator and the number of the heat regenerators are three, and the number of the tenth pipelines is two.
In one embodiment, the third pipeline, the fourth pipeline, the seventh pipeline and the eighth pipeline are all provided with one-way valves for controlling pipeline flow directions.
In one embodiment, the device further comprises a driving motor for driving the piston of the piston to move leftwards or rightwards according to a driving instruction.
In one embodiment, the device further comprises a controller for controlling the pressure adjustment of the pressure adjusting valve and sending a driving command to the driving motor.
In one embodiment, the piston is a hydraulic piston.
In one embodiment, the magnetic system further comprises a permanent magnet group or a superconducting magnet group, and the N pole and the S pole of the magnetic system are respectively arranged at two sides of the plurality of active magnetic regenerators.
The beneficial effects of the invention are as follows: the double-backheating type low-temperature magnetic refrigerating device solves the technical problems that the current liquid hydrogen temperature zone magnetic refrigerating device in the prior art still has single flow path system, large backheating loss, serious heat leakage, huge and compact whole structure, axial heat conduction of heat exchange fluid in a hydraulic piston and the like, and has the following beneficial effects: compared with the existing liquid hydrogen temperature zone magnetic refrigerating device, the right multi-stage heat regenerator and the left multi-stage active magnetic heat regenerator in the device are symmetrically arranged, in addition, the right multi-stage heat regenerator and two shunt branches are additionally arranged on the basis of only the multi-stage active magnetic heat regenerator, so that the heat regenerating performance of the liquid hydrogen temperature zone magnetic refrigerating device is improved, the flow path design is more reasonable, and the cooling performance of the liquid hydrogen temperature zone magnetic refrigerating device can be improved under the optimal flow working condition when the left multi-stage active magnetic heat regenerator works.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are needed in the description of the embodiments or the prior art will be briefly described, and it is obvious that the drawings in the description below are some embodiments of the present invention, and other drawings can be obtained according to the drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of the overall structure of a dual regenerative cryogenic magnetic refrigeration device according to an embodiment of the invention;
wherein, P1: a piston; c1: a low temperature heat exchanger; h1: a high temperature heat exchanger; r31, R21, R11: an active magnetic regenerator; r32, R22, R12: a regenerator; v11, V12, V13, V14: a one-way valve; v21, V22: a pressure regulating valve.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the invention. The components of the embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations. Thus, the following detailed description of the embodiments of the invention, as presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be made by a person skilled in the art without making any inventive effort, are intended to be within the scope of the present invention.
In the description of the embodiments of the present invention, it should be understood that the terms "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the embodiments of the present invention and to simplify the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the embodiments of the present invention.
Hereinafter, a dual regenerative low-temperature magnetic refrigeration apparatus according to an embodiment of the present invention will be specifically described with reference to fig. 1.
As shown in fig. 1, the dual regenerative low-temperature magnetic refrigeration device provided by the embodiment of the invention comprises a plurality of active magnetic regenerators (R31, R21 and R11 in the figure), a plurality of regenerators (R32, R22 and R12 in the figure), a piston P1, a high-temperature heat exchanger H1 and a low-temperature heat exchanger C1, wherein the plurality of active magnetic regenerators are sequentially arranged from a first end to a second end, the magnetic thermal materials filled in each active magnetic regenerator are sequentially reduced, and each active magnetic regenerator is connected in series through a first pipeline; the plurality of regenerators are sequentially arranged from the first end to the second end, the packing in each regenerator is sequentially reduced, each regenerator is connected in series through a second pipeline, and the regenerator (R12 in the figure) at the second end is communicated with the active magnetic regenerator (R11 in the figure) at the second end through a third pipeline; the left cavity of the piston P1 is communicated with the active magnetic heat regenerator at the first end through a fourth pipeline, and the right cavity is filled with heat exchange fluid and is communicated with the heat regenerator at the first end through a fifth pipeline (R32 in the figure); the high-temperature heat exchanger H1 is used for precooling the heat exchange fluid, one end of the high-temperature heat exchanger H1 is communicated with the left cavity of the piston P1 through a sixth pipeline, and the other end of the high-temperature heat exchanger H1 is communicated with the active magnetic regenerator (R31 in the figure) at the first end through a seventh pipeline; the low-temperature heat exchanger C1 is used for liquefying hydrogen to generate refrigeration, one end of the low-temperature heat exchanger C1 is communicated with the active magnetic heat regenerator (R11) at the second end through an eighth pipeline, and the other end of the low-temperature heat exchanger C1 is communicated with the heat regenerator (R12 in the figure) at the second end through a ninth pipeline; the flow direction of the third pipeline is from the heat regenerator to the active magnetic heat regenerator, the flow direction of the fourth pipeline is towards the first end, the flow direction of the seventh pipeline is towards the second end, and the flow direction of the eighth pipeline is from the low-temperature heat exchanger C1 to the active magnetic heat regenerator.
In this embodiment, the third pipeline, the fourth pipeline, the seventh pipeline and the eighth pipeline are all provided with check valves (V11, V12, V13 and V14 in the figure) for controlling the pipeline flow direction, so as to realize that the flow direction of the third pipeline is from the regenerator to the active magnetic regenerator, the flow direction of the fourth pipeline is toward the first end, the flow direction of the seventh pipeline is toward the second end, and the flow direction of the eighth pipeline is from the cryogenic heat exchanger C1 to the active magnetic regenerator.
In the drawings, all pipelines are not marked, the pipeline connected between each active magnetic regenerator is a first pipeline, the pipeline connected between each active magnetic regenerator is a second pipeline, the first end and the second end are virtual directions defined for convenience in describing the claims, the first end can be understood as the upper end in the drawings of the embodiment, the second end can be understood as the lower end in the drawings of the embodiment, it can be understood that from the lowest end to the uppermost end, the magneto-caloric material in each active magnetic regenerator is sequentially increased, the filler in each active magnetic regenerator is sequentially increased, because the uppermost active magnetic regenerator is a high-temperature active magnetic regenerator (R31 in the drawings) of the double-regenerative low-temperature magnetic refrigerator, the thermal load is relatively large, the filled magneto-caloric material is more, and the mass flow rate of heat exchange fluid flowing through the high-temperature active magnetic regenerator R3 is relatively large for bringing all heat generated by the magneto-caloric material in the active magnetic regenerator during the excitation process and cold energy generated by the demagnetizing process; the active magnetic regenerator at the lower end is a low-temperature active magnetic regenerator (R11 in the figure), wherein the filled magnetocaloric material is the least, and similarly, the filler in the regenerator is the same as that in the conventional regenerator.
It should be noted that the filling amount of the magnetocaloric material in each active magnetic regenerator may be designed based on actual scene requirements.
In this embodiment, the number of the active magnetic regenerators is the same as that of the regenerators, and the active magnetic regenerators and the regenerators are correspondingly arranged left and right so that the first pipeline and the second pipeline are mutually corresponding, each corresponding group of the first pipeline and the second pipeline are communicated through tenth pipelines, and each tenth pipeline is provided with a pressure regulating valve (V21 and V22 in the figure).
In this embodiment, the number of the active magnetic heat regenerator and the heat regenerator is three, and the number of the tenth pipeline is two.
In this embodiment, the active magnetic regenerator in the drawing is a low-temperature active magnetic regenerator R11, a medium-temperature active magnetic regenerator R21, and a high-temperature active magnetic regenerator R31 in order from bottom to top, and the active magnetic regenerator is a high-temperature regenerator R32, a medium-temperature regenerator R22, and a low-temperature regenerator R12 in order from top to bottom.
In this embodiment, the left cavity of the piston P1 is communicated with the active magnetic regenerator R31 at the upper end through the fourth pipeline, the heat exchange fluid filled in the right cavity may be helium, the right cavity is communicated with the regenerator R32 at the upper end through the fifth pipeline, because the flow direction of the third pipeline can only be leftward, the flow direction of the fourth pipeline can only be upward, the flow direction of the seventh pipeline can only be downward, and the flow direction of the eighth pipeline can only be rightward, thereby, when the active magnetic regenerator is at the end of excitation and is at the maximum magnetic field, the heat exchange fluid can be blown out by pushing the piston body of the piston to rightward, the heat exchange fluid flows out from the right cavity of the piston, and then the main flow path of the heat exchange fluid sequentially passes through the high-temperature-stage regenerator R32, the medium-temperature-stage regenerator R22, the low-temperature-stage regenerator R12, the check valve V11, the low-temperature-stage active magnetic regenerator R11, the medium-temperature-stage active magnetic regenerator R21, the high-temperature-stage active magnetic regenerator R31 and the check valve V14, and finally flows into the left cavity of the piston P1. When the heat exchange fluid flows through the right multistage heat regenerator, the heat exchange fluid is cooled step by the right three heat regenerators R32, R22 and R12, and the process only relates to the heat regeneration and heat exchange process; when flowing through the left multi-stage active magnetic regenerator, the magnetic energy is heated step by the left three active magnetic regenerators R11, R21 and R31. Similarly, when the demagnetization of the three active magnetic regenerators R11, R21 and R31 on the left is finished at the minimum magnetic field, the piston body of the piston P1 is pushed to start moving leftwards, and the heat exchange fluid flows out of the left cavity of the piston and is cooled by the high-temperature end heat exchanger H1, so that the initial temperature is kept near the liquid nitrogen temperature. The main flow path of the heat exchange fluid sequentially passes through the check valve V13, the high-temperature-stage active magnetic regenerator R31, the medium-temperature-stage active magnetic regenerator R21, the low-temperature-stage active magnetic regenerator R11, the check valve V12, the low-temperature-end heat exchanger C1, the low-temperature-stage regenerator R12, the medium-temperature-stage regenerator R22 and the high-temperature-stage regenerator R32, and finally flows into the right chamber of the piston P1. When the heat exchange fluid flows through the left multi-stage active magnetic heat regenerator, the heat exchange fluid is cooled step by the left three active magnetic heat regenerators R3, R21 and R11, and the process not only relates to the heat regeneration and heat exchange process in the common heat regenerator, but also relates to the magnetocaloric effect process caused by the magnetic field change; when flowing through the right multi-stage regenerator, the heat is heated step by the right three active magnetic regenerators R12, R22 and R32, wherein only the heat regeneration and heat exchange engineering in the common regenerators is involved. It can be understood that the left multi-stage active magnetic regenerator and the right multi-stage regenerator together form a double regeneration process of the liquid hydrogen temperature zone magnetic refrigeration device. The demagnetization end of the left multistage active magnetic heat regenerator is at the minimum magnetic field, and in the clockwise flowing process of the whole main flow path, the heat exchange fluid obtains the minimum temperature in the low-temperature end heat exchanger C1, absorbs heat from the outside, and generates a refrigeration effect.
In this embodiment, the heat load near the high temperature stage is relatively large because the heat load of each stage of active magnetic regenerator is not the same. Therefore, the high-temperature-stage active magnetic regenerator R31 is filled with more magnetocaloric materials, the volume of the active magnetic regenerator R31 is relatively large, and the mass flow rate of the heat exchange fluid flowing through the high-temperature-stage active magnetic regenerator R31 is relatively large in order to take out all the heat generated by the magnetocaloric materials in the active magnetic regenerator R31 during the excitation process and the cold generated by the demagnetizing process. Therefore, a circulation branch formed by a tenth pipeline is arranged between the left multi-stage active magnetic heat regenerator and the right multi-stage heat regenerator, namely, a flow dividing branch (tenth pipeline) is respectively arranged between the left high-temperature-stage active magnetic heat regenerator R31, the middle-temperature-stage active magnetic heat regenerator R21, the right high-temperature-stage heat regenerator R32 and the middle-temperature-stage heat regenerator R22, the mass flow rate of heat exchange fluid in the flow dividing branch between the high-temperature-stage active magnetic heat regenerator R31 and the high-temperature-stage heat regenerator R32 is controlled by arranging a pressure regulating valve V22 on the tenth pipeline, and the mass flow rate of heat exchange fluid in the flow dividing branch between the middle-temperature-stage active magnetic heat regenerator R21 and the middle-temperature-stage heat regenerator R22 is controlled by arranging a pressure regulating valve V21 on the tenth pipeline. The arrangement of the shunt branch can ensure that the heat exchange fluid flowing through the left multi-stage active magnetic heat regenerator is the best mass flow rate, namely, the heat or cold generated by the magneto-caloric material in each stage of active magnetic heat regenerator can be completely taken out, thereby improving the refrigeration efficiency of the liquid hydrogen temperature zone magnetic refrigeration device.
Further, a driving motor (not shown) for driving the piston body of the piston to move leftwards or rightwards according to a driving command is also included. The controller is used for controlling the pressure regulation of the pressure regulating valve and sending a driving instruction to the driving motor.
In one embodiment, the piston is a hydraulic piston.
In one embodiment, the magnetic system further comprises a permanent magnet group or a superconducting magnet group, and the N pole and the S pole of the magnetic system are respectively arranged at two sides of the plurality of active magnetic regenerators.
In particular, the embodiment shown in fig. 1 is described.
As shown in fig. 1, the dual regenerative low-temperature magnetic refrigeration device provided in this embodiment mainly includes a hydraulic piston P1, a low-temperature end heat exchanger (i.e., a low-temperature heat exchanger) C1, a high-temperature end heat exchanger (i.e., a high-temperature heat exchanger) H1, three active magnetic regenerators R11, R21, R31, three regenerators R12, R22, R32, four check valves V11, V12, V13, V14, two pressure regulating valves V21, V22, and a magnet system, all of which are connected through air circuit pipelines.
Here, the magnet system of the dual regenerative cryogenic magnetic refrigerator of the present embodiment includes only one magnet group Mag1, which may be a permanent magnet group or an electromagnet group, which is located outside the left multi-stage active magnetic regenerator. The magnet group Mag1 can generate a variable magnetic field outside the multistage active magnetic heat regenerator, so that the magnetocaloric material in the active magnetic heat regenerator generates a magnetocaloric effect and is matched with the flow of heat exchange fluid in a flow path system, and the double-regenerative low-temperature magnetic refrigeration device generates a refrigeration effect.
The initial temperature of the dual regenerative low temperature magnetic refrigeration device of this embodiment is determined by the set temperature of the high temperature side heat exchanger H1, such as the liquid nitrogen temperature. The high-temperature end heat exchanger H1 can pre-cool heat exchange fluid helium in the liquid hydrogen temperature zone magnetic refrigeration device, the initial temperature is guaranteed to be near the liquid nitrogen temperature, and a small-sized low-temperature refrigerator can be selected to guarantee the temperature of the high-temperature end heat exchanger H1, such as a Stirling engine or a GM refrigerator.
By way of example, in the dual regenerative low temperature magnetic refrigeration device of this embodiment, the parallel symmetrical arrangement structure of the left multi-stage active magnetic regenerator and the right multi-stage regenerator enables the temperature of the heat exchange fluid in the left and right chambers of the hydraulic piston P1 to be kept approximately the same, and reduces the axial heat conduction of the heat exchange fluid in the hydraulic piston P1. In addition, the left multi-stage active magnetic heat regenerator and the right multi-stage heat regenerator are symmetrically arranged in parallel, so that the occupied volume of the magnetic refrigeration device in the liquid hydrogen temperature zone is greatly reduced, and the compactness of the device is improved.
It will be appreciated that when the excitation of the three active magnetic regenerators R11, R21, R31 on the left is terminated at the maximum magnetic field, the hydraulic piston P1 begins to move to the right, pushing the heat exchange fluid in the pipeline in a clockwise direction. The heat exchange fluid flows out of the right chamber of the piston first, then the main flow path of the heat exchange fluid sequentially passes through the high-temperature-stage regenerator R32, the medium-temperature-stage regenerator R22, the low-temperature-stage regenerator R12, the check valve V11, the low-temperature-stage active magnetic regenerator R11, the medium-temperature-stage active magnetic regenerator R21, the high-temperature-stage active magnetic regenerator R31 and the check valve V14 in the multi-stage regenerator, and finally flows into the left chamber of the hydraulic piston P1. When the heat exchange fluid flows through the right multistage heat regenerator, the heat exchange fluid is cooled step by the right three heat regenerators R32, R22 and R12, and the process only relates to the heat regeneration and heat exchange process; when flowing through the left multi-stage active magnetic regenerator, the magnetic energy is heated step by the left three active magnetic regenerators R11, R21 and R31. Likewise, when the end of demagnetization of the three active magnetic regenerators R11, R21, R31 on the left is at the minimum magnetic field, the hydraulic piston P1 starts to move to the left, pushing the heat exchange fluid to flow in the counterclockwise direction in the pipeline. After flowing out of the left chamber of the piston, the heat exchange fluid is cooled by the high-temperature end heat exchanger H1, so that the initial temperature is maintained near the liquid nitrogen temperature. The main flow path of the heat exchange fluid sequentially passes through the check valve V13, the high-temperature-stage active magnetic regenerator R31, the medium-temperature-stage active magnetic regenerator R21, the low-temperature-stage active magnetic regenerator R11, the check valve V12, the low-temperature-end heat exchanger C1, the low-temperature-stage regenerator R12, the medium-temperature-stage regenerator R22 and the high-temperature-stage regenerator R32, and finally flows into the right chamber of the hydraulic piston P1. When the heat exchange fluid flows through the left multi-stage active magnetic heat regenerator, the heat exchange fluid is cooled by the left three active magnetic heat regenerators R31, R21 and R11 step by step, and the process not only relates to the heat regeneration and heat exchange process in the common heat regenerator, but also relates to the magnetocaloric effect process caused by the magnetic field change; when flowing through the right multi-stage regenerator, the heat is heated step by the right three active magnetic regenerators R12, R22 and R32, wherein only the heat regeneration and heat exchange engineering in the common regenerators is involved. The left multi-stage active magnetic regenerator and the right multi-stage regenerator together form a double-regenerative process of the magnetic refrigeration device in the liquid hydrogen temperature zone. The demagnetization end of the left multistage active magnetic heat regenerator is at the minimum magnetic field, and in the clockwise flowing process of the whole main flow path, the heat exchange fluid obtains the minimum temperature in the low-temperature end heat exchanger C1, absorbs heat from the outside, and generates a refrigeration effect.
In this embodiment, the left multi-stage active magnetic regenerator is composed of three active magnetic regenerators R31, R21, R11, respectively, and the right multi-stage regenerator is composed of three common regenerators R32, R22, R12, respectively. Because the heat load of each stage of active magnetic heat regenerator is different in the liquid hydrogen temperature region magnetic refrigeration device, the heat load near the high temperature stage is relatively large. Therefore, the high-temperature-stage active magnetic regenerator R31 is filled with more magnetocaloric materials, the volume of the regenerator is relatively large, and the mass flow rate of the heat exchange fluid flowing through the high-temperature-stage active magnetic regenerator R31 is relatively large in order to take out all the heat generated by the magnetocaloric materials in the regenerator during the excitation process and the cold generated by the demagnetizing process. Therefore, a circulation branch is arranged between the left multi-stage active magnetic heat regenerator and the right multi-stage heat regenerator, namely, a branch is respectively arranged between the left high-temperature-stage active magnetic heat regenerator R31, the middle-temperature-stage active magnetic heat regenerator R21 and the right high-temperature-stage heat regenerator R32 and the middle-temperature-stage heat regenerator R22, the mass flow rate of heat exchange fluid in the branch between the high-temperature-stage active magnetic heat regenerator R31 and the high-temperature-stage heat regenerator R32 is controlled by a pressure regulating valve V22, and the mass flow rate of heat exchange fluid in the branch between the middle-temperature-stage active magnetic heat regenerator R21 and the middle-temperature-stage heat regenerator R22 is controlled by a pressure regulating valve V21. The arrangement of the shunt branch can ensure that the heat exchange fluid flowing through the left multi-stage active magnetic heat regenerator is the best mass flow rate, namely, the heat or cold generated by the magneto-caloric material in each stage of active magnetic heat regenerator can be completely taken out, thereby improving the refrigeration efficiency of the liquid hydrogen temperature zone magnetic refrigeration device.
Therefore, the double-regenerative low-temperature magnetic refrigeration device provided by the embodiment solves the technical problems that the current liquid hydrogen temperature zone magnetic refrigeration device in the prior art still has single flow path system, large regenerative loss, serious heat leakage, huge and compact whole structure, axial heat conduction of heat exchange fluid in a hydraulic piston and the like, and has the following beneficial effects: compared with the existing liquid hydrogen temperature zone magnetic refrigerating device, the right multi-stage heat regenerator and the left multi-stage active magnetic heat regenerator in the device are symmetrically arranged, in addition, the right multi-stage heat regenerator and two shunt branches are additionally arranged on the basis of only the multi-stage active magnetic heat regenerator, so that the heat regenerating performance of the liquid hydrogen temperature zone magnetic refrigerating device is improved, the flow path design is more reasonable, and the cooling performance of the liquid hydrogen temperature zone magnetic refrigerating device can be improved under the optimal flow working condition when the left multi-stage active magnetic heat regenerator works.
In the description of the present invention, furthermore, the terms "first," "second," "another," "yet another" are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more of the described features. In the description of the embodiments of the present invention, the meaning of "plurality" is two or more, unless explicitly defined otherwise.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "connected," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art. Furthermore, in the description of the present invention, unless otherwise indicated, the meaning of "a plurality" is two or more.
While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: many changes, modifications, substitutions and variations may be made to the embodiments without departing from the spirit and principles of the invention, the scope of which is defined by the claims and their equivalents.
Claims (8)
1. A dual regenerative cryogenic magnetic refrigeration device, comprising:
the plurality of active magnetic heat regenerators are sequentially arranged from the first end to the second end, the magneto-thermal materials filled in each active magnetic heat regenerator are sequentially reduced, and each active magnetic heat regenerator is connected in series through a first pipeline;
the heat regenerators are sequentially arranged from the first end to the second end, the packing in each heat regenerator is sequentially reduced, each heat regenerator is connected in series through a second pipeline, and the heat regenerator at the second end is communicated with the active magnetic heat regenerator at the second end through a third pipeline;
the left cavity of the piston is communicated with the active magnetic heat regenerator at the first end through a fourth pipeline, and the right cavity is filled with heat exchange fluid and is communicated with the heat regenerator at the first end through a fifth pipeline;
the high-temperature heat exchanger is used for precooling the heat exchange fluid, one end of the high-temperature heat exchanger is communicated with the left cavity of the piston through a sixth pipeline, and the other end of the high-temperature heat exchanger is communicated with the active magnetic regenerator at the first end through a seventh pipeline;
the low-temperature heat exchanger is used for liquefying hydrogen to generate refrigeration, one end of the low-temperature heat exchanger is communicated with the active magnetic heat regenerator at the second end through an eighth pipeline, and the other end of the low-temperature heat exchanger is communicated with the heat regenerator at the second end through a ninth pipeline;
the flow direction of the third pipeline is from the heat regenerator to the active magnetic heat regenerator, the flow direction of the fourth pipeline is towards the first end, the flow direction of the seventh pipeline is towards the second end, and the flow direction of the eighth pipeline is from the low-temperature heat exchanger to the active magnetic heat regenerator.
2. The dual regenerative cryogenic magnetic refrigeration device of claim 1, wherein the number of active magnetic regenerators is the same as the number of regenerators, and the active magnetic regenerators and the regenerators are arranged in a left-right correspondence manner so that the first pipeline and the second pipeline are in correspondence with each other, each corresponding group of the first pipeline and the second pipeline is communicated through a tenth pipeline, and each tenth pipeline is provided with a pressure regulating valve.
3. The dual regenerative cryogenic magnetic refrigerator of claim 2, wherein the active magnetic regenerator and the regenerator are three, and the tenth pipeline is two.
4. The dual regenerative cryogenic magnetic refrigeration device of claim 2, wherein the third, fourth, seventh and eighth lines are each provided with a check valve for controlling the flow direction of the lines.
5. The dual regenerative cryogenic magnetic refrigerator of claim 4, further comprising a drive motor for driving the piston of the piston to move leftwards or rightwards according to a drive command.
6. The dual regenerative cryogenic magnetic refrigerator of claim 5, further comprising a controller for controlling pressure regulation of the pressure regulating valve, and transmitting a driving command to a driving motor.
7. The dual regenerative cryogenic magnetic refrigerator of claim 1, wherein the piston is a hydraulic piston.
8. The dual regenerative cryogenic magnetic refrigerator of claim 1, further comprising a magnet system comprising a permanent magnet set or a superconducting magnet set, with N and S poles disposed on either side of the plurality of active magnetic regenerators, respectively.
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| CN202310314630.5A CN116379637A (en) | 2023-03-28 | 2023-03-28 | Double-regenerative low-temperature magnetic refrigeration device |
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| CN202310314630.5A CN116379637A (en) | 2023-03-28 | 2023-03-28 | Double-regenerative low-temperature magnetic refrigeration device |
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