A magnetic refrigeration system

Abstract

The utility model provides a kind of magnetic refrigeration system, it is related to refrigeration technical field, solve the technical problem of liquid heat exchange working substance pumping difficulty.The magnetic refrigeration system, including magnetic bed, condenser, evaporator, circulating drive component, hot end liquid accumulator;Magnetic bed quantity is two groups, and each group of magnetic bed has hot channel and cold channel;The hot interface both ends of condenser are communicated with one end of hot channel through heat pipe line respectively;The cold interface both ends of condenser are communicated with one end of cold channel through cold pipe line respectively;Evaporator one end is connected with the other end of cold channel, and the other end of evaporator is connected with circulating drive component;Circulating drive component is connected with the other end of hot channel;Hot end liquid accumulator is arranged between condenser and hot channel.The utility model effectively relieves the pressure fluctuation of liquid heat exchange working substance in circulation process by setting hot end liquid accumulator, reduces pumping resistance, improves system circulation stability.

Description

Technical Field

[0001] This utility model relates to the field of refrigeration technology, and in particular to a magnetic refrigeration system. Background Technology

[0002] Statistics show that nearly 20% of global electricity consumption is used for refrigeration and air conditioning equipment. In recent years, with rising global temperatures and increased energy consumption, new green, environmentally friendly refrigeration technologies with no greenhouse effect potential have attracted much attention. Among them, magnetic refrigeration has been rated as one of the top 10 technologies most likely to replace compression refrigeration.

[0003] For magnetic refrigeration devices, the most crucial aspect is effectively extracting the cooling energy generated by the magnetic working fluid and rapidly establishing a temperature gradient. Existing magnetic refrigeration systems utilize gaseous, liquid, and solid heat exchangers. However, gaseous heat exchangers suffer from low heat exchange efficiency, and solid heat exchangers are currently technically immature, with unresolved issues such as high thermal resistance. Therefore, liquid heat exchangers are commonly used. Water pumps and solenoid valves are employed to switch flow paths, enabling the alternating switching between hot and cold systems.

[0004] The applicant has discovered at least the following technical problems with the existing technology: 1. Due to the alternating hot and cold characteristics of magnetic refrigeration accumulators, extracting their cooling capacity using water is much more complex than with conventional air conditioning systems. For a single accumulator, four solenoid valves are required: two to control the hot channel and two to control the cold channel. Therefore, for multi-bed systems, even more solenoid valves are needed, making control even more complex. 2. Solenoid valves exhibit delays, slow responses, and generate Joule heat when energized. 3. The liquid heat exchange medium is incompressible, leading to difficulties in extraction during the suction process. Therefore, existing magnetic refrigeration systems suffer from system complexity, suction difficulties, solenoid valve delays, heat generation, and slow system cooling (generally taking 10 to 30 minutes to stabilize). Utility Model Content

[0005] The purpose of this invention is to provide a magnetic refrigeration system to solve the technical problem of difficulty in pumping liquid heat exchange working fluid in the prior art.

[0006] To achieve the above objectives, the present invention provides the following technical solution: This utility model provides a magnetic refrigeration system, comprising a magnetic bed, a condenser, an evaporator, a circulation drive assembly, and a hot-end liquid receiver; wherein: The number of magnetic beds is two sets, and each set of magnetic beds has a hot channel and a cold channel; The two ends of the condenser's hot interface are respectively connected to one end of the hot channel via hot pipes; the two ends of the condenser's cold interface are respectively connected to one end of the cold channel via cold pipes. One end of the evaporator is connected to the other end of the cold aisle, and the other end of the evaporator is connected to the circulation drive assembly; The circulation drive component is connected to the other end of the thermal channel; The hot-end liquid reservoir is disposed between the condenser and the hot channel.

[0007] The magnetic refrigeration system provided by this invention effectively alleviates pressure fluctuations of the liquid heat exchange medium during circulation by incorporating a hot-end liquid receiver, reducing suction resistance and improving system circulation stability. Simultaneously, the liquid receiver buffers volume changes caused by thermal expansion and contraction, avoiding start-up difficulties due to the incompressibility of liquids. Combined with a dual-group alternating operation design for the magnetic bed and optimized piping, the number of solenoid valves used is reduced, control logic is simplified, and response speed is improved.

[0008] As a further improvement of this utility model, the hot-end liquid storage device includes a hot-end liquid storage tank and an air valve; wherein: the air valve is installed on the hot-end liquid storage tank to enable communication between the inner cavity of the hot-end liquid storage tank and the atmosphere.

[0009] This invention, by installing a gas valve on the hot-end liquid storage tank, maintains a dynamic balance between the internal pressure and the external atmosphere during system operation, further reducing circulation resistance and effectively preventing the problem of poor liquid flow caused by pressure buildup in a confined space. The gas valve design also automatically compensates for working fluid volume fluctuations caused by temperature changes, improving the stability of system startup and response to varying operating conditions. Simultaneously, it reduces reliance on solenoid valves, simplifies control logic, and makes the entire magnetic refrigeration system more efficient and reliable.

[0010] As a further improvement of this utility model, a first one-way valve is also included, disposed between the hot channel and the hot-end liquid receiver. Through this structural arrangement, the first one-way valve effectively prevents backflow of the liquid heat exchange medium due to pressure changes during circulation, ensuring stable unidirectional flow of the medium and further improving the reliability of system operation. This design prevents the cold-end medium from flowing back into the hot-end liquid receiver during startup, ensuring uniform distribution of the medium within the magnetic bed's hot and cold channels and accelerating the cooling response. Simultaneously, during changes in operating conditions or shutdown, the one-way valve and the hot-end liquid receiver work together to suppress pressure fluctuation transmission, reduce the risk of cavitation, and extend the service life of critical components.

[0011] As a further improvement of this utility model, it also includes a cold-end liquid receiver, which is disposed between the evaporator and the circulation drive assembly.

[0012] Specifically, the cold end liquid receiver includes cold end liquid receiver tanks 701 and 702.

[0013] This invention effectively balances the volume change of the working fluid on the low-temperature side by adding a cold-end liquid receiver, avoiding cavitation or insufficient liquid supply caused by a sudden drop in pressure within the evaporator. The cold-end liquid receiver works in conjunction with the circulation drive components to ensure a stable supply of the low-temperature working fluid, improving the system's responsiveness under transient conditions. Combined with the layout of the hot-end liquid receiver and the first one-way valve, pressure buffering and flow direction control are achieved throughout the circulation path, further improving refrigeration efficiency and operational safety.

[0014] As a further improvement of this utility model, the cold end liquid receiver is connected to both ends of the evaporator through a first pipeline and a second pipeline, respectively.

[0015] This connection method enables the cold-end liquid receiver to bidirectionally adjust the working fluid flow rate, adapt to dynamic changes in the inlet and outlet pressures of the evaporator, and effectively alleviate pipeline stress caused by thermal expansion and contraction under low-temperature conditions.

[0016] As a further improvement of this utility model, a second one-way valve is provided between the evaporator and the cold channel. The second one-way valve ensures that the working fluid flows unidirectionally from the cold-end receiver into the cold channel, effectively preventing the low-temperature working fluid from flowing back to the evaporator during shutdown or changes in operating conditions, thus avoiding heat loss and channel blockage. This design, in conjunction with the cold-end receiver, enhances the system's stability under frequent start-ups and load fluctuations, and improves the heat exchange efficiency on the low-temperature side. Combined with the hot-end gas valve, the first one-way valve, and the dual-pipeline connection structure, a fully controllable working fluid circulation path is constructed. As a further improvement of this utility model, the circulating drive assembly includes a piston cylinder and a drive mechanism; wherein: the drive mechanism is drively connected to the piston in the piston cylinder to drive the piston to reciprocate. The drive mechanism achieves stepless adjustment of the heat exchange medium flow rate by precisely controlling the piston's movement frequency and stroke, adapting to different refrigeration load requirements. The inner wall of the piston cylinder is treated with a low-friction coating to reduce reciprocating motion losses and improve energy utilization efficiency. This structure simplifies traditional pump and valve systems, reduces mechanical failure rates, and enhances the overall reliability of the system.

[0017] As a further improvement of this invention, the circulation drive assembly is connected to the cold-end liquid receiver, which is connected to the other end of the hot channel via a third pipeline. The third pipeline connects the cold-end liquid receiver and the hot channel, forming a closed-loop circulation path to ensure efficient reflux and distribution of the working fluid in the high and low temperature ranges. This arrangement, combined with precise flow control via piston drive, effectively avoids liquid accumulation or vapor lock on the low-temperature side, improving pressure stability during system start-up and shutdown. Simultaneously, the cold-end liquid receiver, through bidirectional buffering, reduces the impact of circulation fluctuations on the piping system, further optimizing the refrigeration response speed and energy efficiency ratio.

[0018] As a further improvement of this utility model, a third one-way valve is provided on the third pipeline. The third one-way valve ensures that the working fluid can only flow in one direction, preventing backflow of the working fluid due to pressure backflow, and avoiding backflow of high-temperature working fluid in the hot channel to the cold end reservoir, which would cause temperature disturbance and heat exchange disorder.

[0019] As a further improvement of this invention, the magnetic bed includes a permanent magnet assembly and a cold accumulator; the permanent magnet assembly is disposed around the periphery of the cold accumulator. The permanent magnet assembly generates a stable alternating magnetic field, driving the magnetic working fluid inside the cold accumulator to undergo a magnetocaloric effect, achieving periodic absorption and release of heat. The cold accumulator is filled with a high specific surface area porous material to enhance the heat exchange efficiency between the magnetic working fluid and the heat exchange fluid. The synergistic design of the permanent magnet assembly and the cold accumulator improves the temperature range and cooling capacity output of the magnetic refrigeration cycle. This structure eliminates the need for an external excitation coil, reducing power consumption and heat generation, and improving the overall energy efficiency of the system. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0021] Figure 1 This is a system composition diagram of the magnetic refrigeration system of this utility model; Figure 2 This is a flow diagram of the magnetic refrigeration system of this utility model in its first state; Figure 3 This is a flow diagram of the magnetic refrigeration system of this utility model in its second state; Figure 4 This is a structural diagram of the cold accumulator in the magnetic refrigeration system of this utility model.

[0022] In the picture: 101, 102, 103, 104, Permanent magnet components; 201, 202, 203, 204, Cold accumulator; 302, 303, 306, 307, First check valve; 304, 308, Second check valve; 301, 305, Third check valve; 401, 402, Hot-end liquid storage tanks; 501. Condenser; 601, 602, Evaporator; 701, 702, Cold End Liquid Storage Tanks; 801. Piston cylinder; 802. Drive mechanism; 2011, Hot Entry; 2012, Cold Exit; 2013, Hot Export; 2014, Cold Entry; 2015, 2016, 2017, 2018, 2019, Magnetic working fluid filling layer. Detailed Implementation

[0023] To make the objectives, technical solutions, and advantages of this utility model clearer, the technical solutions of this utility model will be described in detail below. Obviously, the described embodiments are only a part of the embodiments of this utility model, and not all of them. Based on the embodiments of this utility model, all other implementation methods obtained by those skilled in the art without creative effort are within the scope of protection of this utility model.

[0024] like Figure 1 As shown, this utility model provides a magnetic refrigeration system, including a magnetic bed, a condenser 501, an evaporator 601, 602, a circulation drive assembly, and a hot-end liquid receiver; wherein: There are two sets of magnetic beds, each set of magnetic beds has a hot channel and a cold channel; more specifically, the two ends of the hot channel are a hot outlet 2013 and a hot inlet 2011, and the two ends of the cold channel are a cold outlet 2012 and a cold inlet 2014. The two ends of the heat interface of condenser 501 are connected to one end of the heat channel via heat pipes. Specifically, one end of the heat interface of condenser 501 is connected to the heat outlet 2013 of one set of magnetic beds, and the other end is connected to the heat inlet 2011 of another set of magnetic beds; for example... Figures 1-4 In the magnetic bed, solid arrows represent hot channels, and dashed arrows represent cold channels; The cold interface of condenser 501 is connected to one end of the cold aisle through cold pipes at both ends; specifically, one end of the cold interface of condenser 501 is connected to the cold inlet 2014 of a set of magnetic beds, and the other end of the cold interface of condenser 501 is connected to the cold outlet 2012 of another set of magnetic beds. One end of evaporators 601 and 602 is connected to the other end of the cold aisle, and the other end of evaporators 601 and 602 is connected to the circulation drive assembly; specifically, there are two evaporators 601 and 602, one end of which is connected to the cold outlet 2012 of a set of magnetic beds, and the other end of which is connected to the circulation drive assembly; one end of the other evaporator 601 and 602 is connected to the cold inlet 2014 of another set of magnetic beds, and the other end of which is connected to the circulation drive assembly. The circulation drive assembly is also connected to the other end of the hot channel; specifically, the circulation drive assembly is connected to the hot inlet 2011 of one set of magnetic beds and the hot outlet 2013 of another set of magnetic beds.

[0025] The hot-end liquid receiver is disposed between the condenser 501 and the hot passage. Specifically, there are two hot-end liquid receivers: one located between a set of magnetic beds and the condenser 501, which is connected to the hot outlet 2013 of the set of magnetic beds via a hot pipe; and the other located between another set of magnetic beds and the condenser 501, which is connected to the hot inlet 2011 of the other set of magnetic beds via a hot pipe.

[0026] The magnetic refrigeration system provided by this invention effectively alleviates pressure fluctuations of the liquid heat exchange medium during circulation by incorporating a hot-end liquid receiver, reducing suction resistance and improving system circulation stability. Simultaneously, the liquid receiver buffers volume changes caused by thermal expansion and contraction, avoiding start-up difficulties due to the incompressibility of liquids. Combined with a dual-group alternating operation design for the magnetic bed and optimized piping, the number of solenoid valves used is reduced, control logic is simplified, and response speed is improved.

[0027] In this embodiment, as shown in the attached diagram, each group of magnetic beds consists of two magnetic beds. Therefore, there are a total of four magnetic beds in two groups. The two magnetic beds in each group are connected in parallel.

[0028] As an optional embodiment of this utility model, the hot-end liquid storage device includes hot-end liquid storage tanks 401 and 402 and an air valve; wherein: the air valve is installed on the top of the hot-end liquid storage tanks 401 and 402 to enable communication between the inner cavity of the hot-end liquid storage tanks 401 and 402 and the atmosphere.

[0029] This invention, by installing air valves on the hot-end liquid storage tanks 401 and 402, prevents difficulties in suction caused by liquid incompressibility, maintains a dynamic balance between the internal pressure and the external atmosphere during system operation, further reduces circulation resistance, and effectively avoids problems of poor liquid flow caused by pressure accumulation in a confined space. The air valve is a common valve connecting the inside and outside of the liquid storage tank; its design also automatically compensates for fluctuations in working fluid volume caused by temperature changes, improves the stability of system startup and response to changing operating conditions, reduces reliance on solenoid valves, simplifies control logic, and makes the entire magnetic refrigeration system more efficient and reliable.

[0030] To prevent backflow during flow path switching, first one-way valves 302, 303, 306, and 307 are also included, which are installed between the hot channel and the hot end reservoir.

[0031] Through the above structural design, the first one-way valves 302, 303, 306, and 307 effectively prevent backflow of the liquid heat exchange medium during circulation due to pressure changes, ensuring stable unidirectional flow of the medium and further improving the reliability of system operation. This design prevents the cold-end medium from flowing back into the hot-end reservoir during startup, ensuring uniform distribution of the medium within the magnetic bed's hot and cold channels and accelerating the cooling response. Simultaneously, during changes in operating conditions or shutdown, the one-way valves and the hot-end reservoir work together to suppress pressure fluctuation transmission, reduce cavitation risk, and extend the service life of critical components.

[0032] Furthermore, it also includes a cold-end liquid receiver, which is located between the evaporators 601 and 602 and the circulation drive assembly. Specifically, there are two cold-end liquid receivers, each connected to one of the two chambers of the circulation drive assembly.

[0033] This invention effectively balances the volume change of the working fluid on the low-temperature side by adding a cold-end liquid receiver, avoiding cavitation or insufficient liquid supply caused by a sudden pressure drop in evaporators 601 and 602. The cold-end liquid receiver works in conjunction with the circulation drive components to ensure a stable supply of the low-temperature working fluid and improve the system's responsiveness under transient conditions. Combined with the layout of the hot-end liquid receiver and the first one-way valves 302, 303, 306, and 307, pressure buffering and flow direction control are achieved throughout the circulation path, further improving refrigeration efficiency and operational safety.

[0034] Specifically, the cold-end liquid receiver is connected to both ends of the evaporators 601 and 602 via the first and second pipes, respectively. This structural arrangement creates a bypass flow path between the cold-end liquid receiver, the evaporators 601 and 602, and the magnetic bed. This not only improves efficiency and avoids delays but also simplifies the structure and effectively mitigates the interference of pressure fluctuations at the inlet of the evaporators 601 and 602 on the flow of the working fluid in the magnetic bed.

[0035] This connection method enables the cold-end liquid receiver to bidirectionally adjust the working fluid flow rate, adapt to the dynamic changes in the inlet and outlet pressures of evaporators 601 and 602, and effectively alleviate pipeline stress caused by thermal expansion and contraction under low-temperature conditions.

[0036] As a further improvement of this utility model, a second one-way valve 304, 308 is provided between the evaporators 601, 602 and the cold aisle. Furthermore, a cold-end liquid receiver is connected between the evaporators 601, 602 and the second one-way valve 304, 308.

[0037] The second one-way valves 304 and 308 ensure that the working fluid flows unidirectionally from the cold-end receiver into the cold aisle, effectively preventing the low-temperature working fluid from flowing back to the evaporators 601 and 602 during shutdowns or changes in operating conditions, thus avoiding heat loss and flow channel blockage. This design works in conjunction with the cold-end receiver to enhance the system's stability under frequent start-ups and load fluctuations, and improve the heat exchange efficiency on the low-temperature side. Combined with the hot-end gas valve, the first one-way valves 302, 303, 306, and 307, and the dual-pipeline connection structure, a fully controllable working fluid circulation path is constructed. As an optional embodiment of this utility model, the circulating drive assembly includes a piston cylinder 801 and a drive mechanism 802; wherein, the drive mechanism 802 is connected to the piston in the piston cylinder 801 to drive the piston to reciprocate. The drive mechanism 802 can be implemented using a crank-rocker or a linear motor, that is, using a crank-rocker or a linear motor to drive the piston to realize the reversal of the fluid in the system, thereby eliminating the need for a solenoid valve; of course, the piston cylinder 801 is also called a bidirectional piston pump, which realizes the reversal of the flow path in the system through the reciprocating motion of the piston, thus eliminating the need for a solenoid valve and simplifying the system; at the same time, the addition of a bypass flow path is beneficial to the rapid formation of a warm cross; the inner wall of the piston cylinder 801 is treated with a low-friction coating to reduce reciprocating motion losses and improve energy utilization efficiency. This structure simplifies the traditional pump and valve system, reduces the mechanical failure rate, enhances the overall reliability of the system, eliminates the need for the original pump and valve combination, and solves the heat generation problem.

[0038] In this embodiment, the circulation drive component is connected to the cold-end liquid receiver, which is connected to the other end of the hot channel via a third pipeline. The third pipeline connects the cold-end liquid receiver and the hot channel, forming a closed-loop circulation path to ensure efficient reflux and distribution of the working fluid across the high and low temperature ranges. This arrangement, combined with precise flow control via piston drive, effectively avoids liquid accumulation or vapor lock on the low-temperature side, improving pressure stability during system start-up and shutdown. Simultaneously, the cold-end liquid receiver, through bidirectional buffering, reduces the impact of circulation fluctuations on the piping system, further optimizing the cooling response speed and energy efficiency ratio.

[0039] Furthermore, a third check valve 301 and 305 are installed on the third pipeline. The installation of the third check valve 301 and 305 ensures that the working fluid can only flow in one direction, preventing backflow of the working fluid due to pressure backflow, and avoiding backflow of high-temperature working fluid in the hot channel to the cold end liquid receiver, which would cause temperature disturbance and heat exchange disorder.

[0040] As a further improvement of this utility model, the magnetic bed includes permanent magnet assemblies 101, 102, 103, 104 and cold accumulators 201, 202, 203, 204; the permanent magnet assemblies 101, 102, 103, 104 are disposed around the cold accumulators 201, 202, 203, 204.

[0041] Furthermore, the cold storage units 201, 202, 203, and 204 each contain several sequentially arranged magnetic working material filling layers 2015, 2016, 2017, 2018, and 2019, such as... Figure 4 As shown, there are five magnetic working fluid filling layers: 2015, 2016, 2017, 2018, and 2019. Permanent magnet components 101, 102, 103, and 104 generate a stable alternating magnetic field, driving the magnetic working fluid within the cold storage units 201, 202, 203, and 204 to undergo a magnetocaloric effect, achieving periodic heat absorption and release. Cold storage units 201, 202, 203, and 204 are filled with a high specific surface area porous material to enhance the heat exchange efficiency between the magnetic working fluid and the heat exchange fluid. The synergistic design of permanent magnet components 101, 102, 103, and 104 with cold storage units 201, 202, 203, and 204 improves the temperature range and cooling capacity output of the magnetic refrigeration cycle. This structure eliminates the need for an external excitation coil, reducing power consumption and heat generation, and improving the overall energy efficiency of the system.

[0042] Taking the cold storage unit 201 as an example, a detailed explanation will be given, such as... Figure 4 As shown, the cold accumulator 201 includes four ports: a hot inlet 2011, a hot outlet 2013, a cold inlet 2014, and a cold outlet 2012. The cold accumulator is filled with Gd and its alloys or LaFeSi materials, which are granular, sheet-like, or porous media. Taking gadolinium alloy as an example, it is divided into 5 or more layers (magnetic working material filling layers 2015-2019) from the hot inlet 2011 to the hot outlet 2013. The Curie temperature difference between adjacent layers is 2-5K, such as 9℃, 13℃, 17℃, 21℃, and 25℃. The temperature change is greatest when the magnetic working material works near its own Curie temperature, and the further it deviates, the less heat it absorbs or releases. When the cold accumulator is magnetized, the magnetic working fluid releases heat. Since the initial temperature is the same from left to right, the temperature of the magnetic working fluid increases from left to right. At this time, the fluid at temperature T1 flows through the hot inlet 2011, absorbs heat from the magnetic working fluid, its temperature rises, and it flows out through the hot outlet 2013. Therefore, when the fluid temperature and the magnetic working fluid temperature are stable, a stable temperature difference, i.e., a temperature gradient, can be formed, resulting in optimal heat exchange; conversely, the opposite is also true. Therefore, lowering the inlet fluid temperature during hot blowing allows for a faster formation of a stable temperature gradient, resulting in a larger temperature difference in the initial stage and better heat exchange.

[0043] This invention's magnetic refrigeration system incorporates a liquid receiver and a gas valve to prevent suction difficulties caused by liquid incompressibility. It also adds a bypass flow path to the evaporator, ensuring the stability of the initial fluid temperature for both hot and cold flows, reducing the inlet fluid temperature during the hot blowing process, facilitating rapid temperature gradient formation, and shortening the time required for temperature gradient formation within the regenerator (due to the added bypass flow path). Furthermore, the addition of liquid receivers before the condenser and after the evaporator not only ensures the stability of the initial fluid temperature for both hot and cold flows but also balances the system pressure difference, reducing the operating resistance of the diaphragm pump / mechanical pump / plunger pump.

[0044] How to use: During the operation of the magnetic system (prototype), the rotation of the permanent magnet assembly keeps half of the cold accumulator in the magnetic field (magnetized state) and the other half out of the magnetic field (demagnetized state). Through this magnetization and demagnetization transition, the temperature difference of the magnetic working fluid can reach 2-3K, or even greater. In the designed magnetic refrigeration system (such as...) Figure 1 As shown), it includes two sets of magnetizing beds and two sets of demagnetizing beds, for a total of four; as shown Figure 2 As shown, when the piston moves to the left, the fluid flows along the solid line. At this time, the two accumulators on the left, 201 and 202, are in a magnetized state, while the two accumulators on the right, 203 and 204, are in a demagnetized state. This is the first state. Figure 3 As shown, when the piston moves to the right, the fluid flows along the dotted line. The accumulators 203 and 204 are in a magnetized state, while the accumulators 201 and 202 are in a demagnetized state. This is the second state. The two states will now be described separately.

[0045] like Figure 2As shown, when the piston cylinder 801 moves to the left, the compressed liquid flows through the closed cold-end liquid storage tank 702, and the liquid temperature is T1 at this time. The liquid then flows through the third one-way valve 301 to the regenerators 201 and 202 respectively, and flows through the heat channels of the regenerators. At this time, the regenerators 201 and 202 are located in the magnetic field of the permanent magnet assemblies 101 and 102, which are exactly in the magnetization state. The magnetic working medium changes in entropy and releases heat. The released heat is carried away by the fluid, and converges into the hot-end liquid storage tank 401 through the first one-way valve 302. Since the inside of the hot-end liquid storage tank 401 is connected to the external atmosphere, the pressure inside the hot-end liquid storage tank 401 is normal pressure. The piston in the piston cylinder 801 moves to the left, causing the liquid in the hot-end liquid storage tank 401 to flow into the piston cylinder 801 along the solid line. Firstly, the temperature of the liquid in the hot-end liquid storage tank 401 is T2, and the temperature becomes T0 after sufficient heat exchange through the condenser 501; after heat exchange, the fluid flows in from the cold inlets of the regenerators 203 and 204. At this time, the regenerators 203 and 204 just leave the magnetic field, the magnetic working medium absorbs heat and the temperature decreases, the fluid exchanges heat after passing through, and the temperature becomes Tc; the low-temperature fluid passes through the second one-way valve 304, part of it flows through the evaporator 601 for heat exchange and the temperature becomes T3, and another part directly flows into the cold-end liquid storage tank 701 through the bypass branch, mixes with the fluid that has passed through the heat exchanger, and the temperature becomes T1; As Figure 3 shown, with the movement of the magnet, the magnet changes from the left state to the right state; at the same time, the piston cylinder moves to the right, driving the fluid with temperature T1 (Tc<T1<T0) to flow through the magnetization beds (regenerators 203 and 204) and then converge into the hot-end liquid storage tank 402. After heat exchange, the fluid flows through the demagnetization beds (regenerators 201 and 202) and finally returns to the cold-end liquid storage tank 702; The driving mechanism drives the piston cylinder 801 to reciprocate, which enables the regenerator to continuously generate cold capacity. The driving mechanism can be a crank rocker, a motor, etc., and the piston cylinder can also be a plunger pump or a diaphragm pump.

[0046] First of all, it needs to be explained here that "inward" refers to the direction toward the center of the accommodation space, and "outward" refers to the direction away from the center of the accommodation space.

[0047] In the description of the present utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and other indicated orientations or positional relationships are based on the appended Figure 1 illustrations, which are only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the referred device or element must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the present utility model.

[0048] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this utility model, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0049] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0050] In this utility model, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0051] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0052] The above description is merely a specific embodiment of this utility model, but the protection scope of this utility model is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this utility model should be included within the protection scope of this utility model. Therefore, the protection scope of this utility model should be determined by the protection scope of the claims.

Claims

1. A magnetic refrigeration system, characterized in that, Includes a magnetic bed, condenser, evaporator, circulation drive assembly, and hot-end liquid receiver; wherein: The number of magnetic beds is two sets, and each set of magnetic beds has a hot channel and a cold channel; The two ends of the condenser's hot interface are respectively connected to one end of the hot channel via hot pipes; the two ends of the condenser's cold interface are respectively connected to one end of the cold channel via cold pipes. One end of the evaporator is connected to the other end of the cold aisle, and the other end of the evaporator is connected to the circulation drive assembly; The circulation drive component is connected to the other end of the thermal channel; The hot-end liquid reservoir is disposed between the condenser and the hot channel.

2. The magnetic refrigeration system according to claim 1, characterized in that, The hot-end liquid storage device includes a hot-end liquid storage tank and an air valve; wherein: the air valve is installed on the hot-end liquid storage tank to enable communication between the inner cavity of the hot-end liquid storage tank and the atmosphere.

3. The magnetic refrigeration system according to claim 1, characterized in that, It also includes a first check valve disposed between the hot channel and the hot end reservoir.

4. The magnetic refrigeration system according to claim 1, characterized in that, It also includes a cold-end liquid receiver disposed between the evaporator and the circulation drive assembly.

5. The magnetic refrigeration system according to claim 4, characterized in that, The cold end liquid receiver is connected to both ends of the evaporator via a first pipeline and a second pipeline, respectively.

6. The magnetic refrigeration system according to claim 1, characterized in that, A second one-way valve is provided between the evaporator and the cold aisle.

7. The magnetic refrigeration system according to claim 5, characterized in that, The cyclic drive assembly includes a piston cylinder and a drive mechanism; wherein the drive mechanism is connected to the piston in the piston cylinder to drive the piston to reciprocate.

8. The magnetic refrigeration system according to claim 4, characterized in that, The circulation drive assembly is connected to the cold end liquid reservoir, which is connected to the other end of the hot channel via a third pipeline.

9. The magnetic refrigeration system according to claim 8, characterized in that, A third check valve is installed on the third pipeline.

10. The magnetic refrigeration system according to claim 1, characterized in that, The magnetic bed includes a permanent magnet assembly and a cold accumulator; the permanent magnet assembly is disposed around the cold accumulator.

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