Magnetic screw driven thermoacoustic refrigeration system and method

Abstract

The application relates to the technical field of low-temperature refrigeration, and provides a magnetic screw drive thermal-acoustic refrigeration system and method, which comprises at least one thermal-acoustic refrigeration basic unit, the unit comprising a pressure wave generating device, a thermal-acoustic refrigerator and a resonance tube. The pressure wave generating device comprises a pressure-resistant shell, a rotating motor, a magnetic screw shaft, a mover permanent magnet, a compression piston and a rotor permanent magnet arranged on the magnetic screw shaft; the magnetic screw shaft is connected with the rotating motor, the compression piston is arranged in the pressure-resistant shell, the mover permanent magnet is connected with the compression piston and is arranged in opposite interval with the rotor permanent magnet; a compression cavity is formed between the compression piston and the pressure-resistant shell; and the resonance tube is communicated with the compression cavity and the thermal-acoustic refrigerator. The rotating motor is used as a power source, the pressure wave generating device is used to replace a linear compressor, the manufacturing difficulty and cost are reduced, the rotating motor has high power density and high magnetic coupling efficiency, a large sound power can be output in a small volume, and the demand for high refrigeration capacity density is met.

Description

Technical Field

[0001] This invention relates to the field of cryogenic refrigeration technology, and in particular to a thermoacoustic refrigeration system and method driven by a magnetic screw. Background Technology

[0002] Against the backdrop of global efforts to address climate change and promote energy conservation and emission reduction, developing environmentally friendly and highly reliable new refrigeration technologies has become an important direction for the refrigeration field. Thermoacoustic refrigeration technology, a novel refrigeration method based on the thermoacoustic effect to achieve the mutual conversion of heat and sound energy, uses acoustic power to drive gas through a compression-expansion cycle in a regenerator, realizing the transport of heat from the low-temperature end to the high-temperature end. Compared with traditional refrigeration technologies, thermoacoustic refrigerators typically use inert gases such as helium and nitrogen as working fluids, with ozone depletion potential (ODP) and global warming potential (GWP) both being 0, exhibiting excellent environmental performance. Furthermore, this system requires no lubricating oil, has a simple structure, and has no moving mechanical parts at the low-temperature end, thus possessing outstanding advantages such as high reliability and long service life.

[0003] In the present technology, the driving methods of thermoacoustic refrigerators mainly include two categories: electric drive and thermal drive. The electric drive method usually uses a linear compressor to provide pressure waves, i.e., acoustic power, to the refrigerator; the thermal drive method relies on the self-excited oscillation of a thermoacoustic motor to generate sound waves to provide acoustic power to the refrigerator.

[0004] However, with the continuous development of thermoacoustic refrigeration technology and the expansion of its application scenarios, the two existing driving methods have revealed the following technical shortcomings: The mainstream electric drive system uses linear compressors. As refrigeration power demands increase, the required output power of linear compressors also increases, leading to a significant increase in piston area and mover mass. Consequently, the technical challenges in high-precision linear support, gap sealing, magnetic circuit design, and vibration suppression are becoming increasingly prominent. Furthermore, linear compressors have not yet achieved large-scale mass production. Limited by stringent gap sealing requirements, complex piston support structures, and the need for large quantities of expensive magnetic circuit materials, the manufacturing cost of linear compressors is relatively high.

[0005] The thermal drive method requires the use of a thermoacoustic engine to generate pressure fluctuations, resulting in a large overall system size and a relatively low power density, making it difficult to meet the application requirements of refrigeration equipment for high cooling capacity density. Summary of the Invention

[0006] This invention aims to solve at least one of the technical problems existing in related technologies. To this end, this invention proposes a magnetic screw-driven thermoacoustic cooling system that can reduce manufacturing difficulty and cost, facilitate mass production, achieve high power output in a small volume, and meet the requirements of high cooling capacity density.

[0007] This invention also proposes a thermoacoustic cooling method driven by a magnetic screw.

[0008] A magnetic screw-driven thermoacoustic cooling system according to an embodiment of the present invention includes at least one thermoacoustic cooling basic unit, wherein the thermoacoustic cooling basic unit includes: A pressure wave generating device includes a pressure-resistant housing, a rotary motor, and a magnetic coupling transmission mechanism disposed within the pressure-resistant housing. The magnetic coupling transmission mechanism includes a magnetic lead screw shaft, a moving permanent magnet, a compression piston, and a rotor permanent magnet disposed on the magnetic lead screw shaft. The magnetic lead screw shaft is drivenly connected to the output end of the rotary motor. The compression piston is reciprocating linearly within the pressure-resistant housing. The moving permanent magnet is connected to the compression piston and arranged at a distance from the rotor permanent magnet. A compression cavity is formed between the compression piston and the pressure-resistant housing. Thermoacoustic refrigerator, including thermoacoustic heat exchange components for performing thermoacoustic energy conversion; A resonant tube, which is connected to the compression cavity and the thermoacoustic refrigerator respectively and forms acoustic coupling; The rotary motor drives the magnetic lead screw shaft and the rotor permanent magnet to rotate. Through the magnetic field coupling between the rotor permanent magnet and the moving permanent magnet, the rotational mechanical energy of the rotary motor is converted into the reciprocating linear motion of the compression piston to generate acoustic power. The acoustic power drives the thermoacoustic refrigerator to perform a refrigeration cycle in the form of alternating gas pressure fluctuations via the resonant tube.

[0009] According to one embodiment of the present invention, the pressure wave generating device further includes: A piston rod, which is connected to the side of the compression piston away from the rotary motor; An elastic element has a first end disposed on the inner wall of the pressure-resistant housing and a second end connected to the end of the piston rod away from the compression piston. The elastic element is used to provide a restoring force to the compression piston for reciprocating linear motion.

[0010] According to one embodiment of the present invention, the pressure wave generating device further includes: A gas bearing or a magnetic levitation bearing is disposed between the compression piston and the pressure-resistant housing.

[0011] According to one embodiment of the present invention, the gap between the rotor permanent magnet and the mover permanent magnet is 1 mm to 4 mm.

[0012] According to one embodiment of the present invention, the thermoacoustic heat exchange assembly includes a cold-end heat exchanger, a regenerator, and a room-temperature heat exchanger connected in sequence. The cold-end heat exchanger, the regenerator, and the room-temperature heat exchanger are all built into the resonant tube, and the compression chamber is connected to one end of the resonant tube near the cold-end heat exchanger.

[0013] According to one embodiment of the present invention, the thermoacoustic heat exchange assembly includes a room temperature end heat exchanger, a regenerator, a cold end heat exchanger, a thermal buffer tube, and a sub-room temperature end heat exchanger connected in sequence; the thermoacoustic refrigerator further includes a feedback tube, which is connected between the sub-room temperature end heat exchanger and the room temperature end heat exchanger to form an acoustic loop structure; the first end of the resonant tube is connected to the compression cavity, and the second end of the resonant tube is connected to the feedback tube.

[0014] According to one embodiment of the present invention, the thermoacoustic refrigeration basic unit has at least three units, and the thermoacoustic refrigerators of two adjacent thermoacoustic refrigeration basic units are connected through the resonant tube to form a traveling wave thermoacoustic loop. Each thermoacoustic refrigerator contains a thermoacoustic heat exchange component comprising a secondary room temperature end heat exchanger, a heat buffer tube, a cold end heat exchanger, a regenerator, and a room temperature end heat exchanger connected in sequence. The pressure wave generating device is connected to the resonant tube, and the compression chamber is connected to the resonant tube.

[0015] According to one embodiment of the present invention, each of the thermoacoustic refrigeration basic units includes two pressure wave generating devices, which are coaxially arranged and opposite to each other, and the compression chambers of the two pressure wave generating devices are connected.

[0016] The magnetic screw-driven thermoacoustic cooling method according to embodiments of the present invention is applied to the magnetic screw-driven thermoacoustic cooling system described in any one of the above claims, the method comprising: The rotary motor is controlled to operate at a preset speed to output rotational mechanical energy, which is used to drive the magnetic lead screw shaft and the rotor permanent magnet to rotate continuously. By utilizing the magnetic field coupling between the rotating rotor permanent magnet and the moving permanent magnet, the rotational mechanical energy of the rotor permanent magnet is converted into the reciprocating linear motion of the compression piston; The compression piston reciprocates linearly within the pressure-resistant housing, periodically compressing and expanding the working gas filling the compression chamber, converting mechanical energy into acoustic energy in the form of alternating gas pressure fluctuations. The acoustic power drives the thermoacoustic refrigerator to perform a refrigeration cycle via the resonant tube.

[0017] According to one embodiment of the present invention, controlling the rotary motor to operate at a preset speed includes: Obtain the acoustic resonant frequency of the thermoacoustic refrigeration system; The target matching speed is determined based on the acoustic resonant frequency and the magnetic pole lead of the magnetic coupling transmission mechanism; Adjust the rotational speed of the rotary motor to the target matching speed.

[0018] The above-described one or more technical solutions in the embodiments of the present invention have at least one of the following technical effects: By employing a rotary motor as the power source and utilizing the non-contact magnetic field coupling between the rotor permanent magnet on the magnetic screw shaft and the mover permanent magnet on the compression piston, rotational motion is efficiently converted into the reciprocating linear motion of the compression piston to generate acoustic power, which in turn drives the thermoacoustic refrigerator to produce a cooling effect. In this way, replacing the linear compressor with a rotary motor and magnetic coupling transmission mechanism avoids the engineering challenges faced by existing electrically driven thermoacoustic refrigerators in areas such as high-precision linear support, gap sealing, magnetic circuit design, and vibration suppression. This reduces the system's manufacturing difficulty and production cost, facilitating large-scale mass production. Simultaneously, due to the high power density of the rotary motor and the high energy transfer efficiency of the magnetic coupling transmission mechanism, the low power density and large size problems caused by the introduction of a thermoacoustic engine in existing thermally driven thermoacoustic refrigerators are avoided. This allows for the output of a large amount of acoustic power within a smaller volume, meeting the application requirements of refrigeration equipment for high cooling capacity density, and facilitating system miniaturization and integration.

[0019] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in the embodiments of the present invention or related technologies, the drawings used in the description of the embodiments or related technologies will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention and are not considered as limitations on this application. Moreover, those skilled in the art can obtain other drawings based on these drawings without creative effort.

[0021] Figure 1 This is one of the schematic structural diagrams of the magnetic screw-driven thermoacoustic cooling system provided by the present invention.

[0022] Figure 2 This is a schematic structural diagram of the magnetic coupling transmission mechanism provided by the present invention.

[0023] Figure 3 This is a schematic flowchart of the thermoacoustic cooling method driven by a magnetic screw provided by the present invention.

[0024] Figure 4This is the second schematic structural diagram of the thermoacoustic cooling system driven by the magnetic screw provided by the present invention.

[0025] Figure 5 This is the third schematic structural diagram of the thermoacoustic cooling system driven by the magnetic screw provided by the present invention.

[0026] Figure 6 This is a schematic structural diagram of the basic thermoacoustic refrigeration unit provided by the present invention.

[0027] Figure label: 01. Basic unit for thermoacoustic refrigeration; 1. Heat buffer tube; 2. Sub-room temperature end heat exchanger; 3. Rotary motor; 4. Pressure-resistant shell; 5. Back cavity; 6. Motor shaft; 7. Cold end heat exchanger; 8. Regenerator; 9. Room temperature end heat exchanger; 10. Piston rod; 11. Compression piston; 12. Magnetic lead screw shaft; 13. Mover permanent magnet; 14. Rotor permanent magnet; 15. Compression chamber; 16. Elastic element; 17. Resonant tube; 18. Feedback tube. Detailed Implementation

[0028] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0029] The specific terms used in this specification are for illustrative purposes only and are not intended to limit the illustrated embodiments. For example, expressions such as "same" and "identical" not only indicate a strictly identical state, but also indicate a state with tolerances or differences in the degree of functionality. For example, expressions indicating relative or absolute arrangement such as "in a certain direction," "along a certain direction," "side by side," "perpendicular," "centered on," "concentric," or "coaxial" not only strictly indicate such an arrangement, but also indicate a state of relative displacement by tolerances or angles or distances with the same degree of functionality.

[0030] The terms “center,” “longitudinal,” “lateral,” “length,” “width,” “thickness,” “upper,” “lower,” “front,” “rear,” “left,” “right,” “vertical,” “horizontal,” “top,” “bottom,” “inner,” “outer,” “clockwise,” “counterclockwise,” “axial,” “radial,” and “circumferential” indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the present invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting the present invention.

[0031] Furthermore, features specified as "first" or "second" may explicitly or implicitly include one or more of those features. In the description of this invention, unless otherwise stated, "multiple" means two or more. In the description of the embodiments of this application, "multiple" means two or more, unless otherwise explicitly specified. In the description of the embodiments of this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, B1 and / or B2 can represent: B1 existing alone, B1 and B2 existing simultaneously, and B2 existing alone. Additionally, the character " / " in this document generally indicates that the preceding and following related objects have an "or" relationship.

[0032] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; 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; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0033] The following is combined Figures 1 to 6 The present invention describes a magnetic screw-driven thermoacoustic cooling system and method.

[0034] Example 1 An embodiment of the first aspect of the present invention provides a magnetically driven thermoacoustic cooling system, such as... Figure 1 and Figure 2 As shown, the system includes at least one thermoacoustic refrigeration basic unit. Each thermoacoustic refrigeration basic unit includes a pressure wave generator, a thermoacoustic refrigerator, and a resonant tube 17. The pressure wave generator is used to generate alternating gas pressure fluctuations (i.e., acoustic power). The thermoacoustic refrigerator consumes the alternating gas pressure fluctuations and completes the refrigeration cycle accordingly.

[0035] The pressure wave generating device includes a pressure-resistant housing 4, a rotary motor 3, and a magnetic coupling transmission mechanism disposed within the pressure-resistant housing 4. The magnetic coupling transmission mechanism includes a magnetic lead screw shaft 12, a rotor permanent magnet 14, a mover permanent magnet 13, and a compression piston 11 disposed on the magnetic lead screw shaft 12. The magnetic lead screw shaft 12 is connected to the output end of the rotary motor 3. The compression piston 11 is disposed within the pressure-resistant housing 4 and can reciprocate linearly. The mover permanent magnet 13 is connected to the compression piston 11 and is arranged at a distance from the rotor permanent magnet 14. A compression chamber 15 is formed between the compression piston 11 and the pressure-resistant housing 4. The thermoacoustic refrigerator includes a thermoacoustic heat exchange component for thermoacoustic energy conversion. The resonant tube 17 is connected to the compression chamber 15 and the thermoacoustic refrigerator respectively and forms acoustic coupling. The rotary motor 3 drives the magnetic lead screw shaft 12 and the rotor permanent magnet 14 to rotate. Through the magnetic field coupling between the rotor permanent magnet 14 and the moving permanent magnet 13, the rotational mechanical energy of the rotary motor 3 is converted into the reciprocating linear motion of the compression piston 11 to generate acoustic power. The acoustic power drives the thermoacoustic refrigerator to perform a refrigeration cycle in the form of alternating gas pressure fluctuations through the resonant tube 17.

[0036] Understandably, the rotary motor 3 serves as the power source for the entire system, providing rotational mechanical energy. The pressure housing 4 has a containment cavity to house the magnetically coupled transmission mechanism and can withstand the alternating pressure generated by the internal gaseous working fluid during system operation. The pressure housing 4 can be made of metallic materials (such as stainless steel or aluminum alloy) to ensure sufficient strength and sealing.

[0037] The compression piston 11 is positioned within the receiving cavity of the pressure-resistant housing 4 in a reciprocating linear motion manner. The side of the compression piston 11 facing away from the rotary motor 3 and the inner wall of the pressure-resistant housing 4 enclose a compression chamber 15. When the compression piston 11 reciprocates, the volume of the compression chamber 15 changes periodically, thereby generating alternating gas pressure fluctuations within the compression chamber 15. These pressure fluctuations constitute the acoustic power used to drive the thermoacoustic refrigerator.

[0038] The magnetic lead screw shaft 12 is arranged along the axial direction of the compression piston 11. The first end of the magnetic lead screw shaft 12 is connected to the output end of the rotary motor 3. The second end of the magnetic lead screw shaft 12 faces the compression piston 11. The rotor permanent magnet 14 is fixedly sleeved on the outer surface of the second end of the magnetic lead screw shaft 12. The function of the magnetic lead screw shaft 12 is to transmit the rotational motion output by the rotary motor 3 to the rotor permanent magnet 14 located on the compression piston 11.

[0039] The moving permanent magnet 13 is fixed to the compression piston 11. As a driven component, the moving permanent magnet 13 receives magnetic force from the rotor permanent magnet 14, thereby driving the compression piston 11 to reciprocate linearly along the axial direction. The rotor permanent magnet 14 and the moving permanent magnet 13 are arranged opposite each other in the radial direction, that is, they are separated by an air gap and do not have direct mechanical contact. The purpose of this relative arrangement is to establish a magnetic coupling channel. When the rotor permanent magnet 14 rotates, the rotating magnetic field it generates will pass through the air gap and act on the moving permanent magnet 13, thereby applying a magnetic torque to the moving permanent magnet 13.

[0040] The resonant tube 17 is connected to the compression chamber 15 of the pressure wave generator and the thermoacoustic refrigerator, respectively, and forms acoustic coupling.

[0041] When the system starts, the rotary motor 3 outputs rotational torque, which drives the rotor permanent magnet 14 of the magnetic screw to rotate through the magnetic screw shaft 12. Due to the magnetic coupling between the rotor permanent magnet 14 and the mover permanent magnet 13, and because the mover permanent magnet 13 is fixedly connected to the compression piston 11, the compression piston 11 can only make reciprocating linear motion along the axial direction (it cannot rotate circumferentially). Therefore, the rotational torque is converted into axial thrust, which drives the mover permanent magnet 13 and the compression piston 11 to start reciprocating linear motion.

[0042] Thus, the rotational mechanical energy output by the rotary motor 3 is converted into the reciprocating linear motion mechanical energy (i.e., acoustic work) of the compression piston 11 through non-contact magnetic coupling between the rotor permanent magnet 14 and the mover permanent magnet 13. The reciprocating motion of the compression piston 11 periodically changes the volume of the compression chamber 15. When moving towards the compression chamber 15, the volume decreases, the gas is compressed, and the pressure increases; when moving away from the compression chamber 15, the volume increases, the gas expands, and the pressure decreases, thereby generating alternating gas pressure fluctuations within the compression chamber 15. These pressure fluctuations are transmitted to the thermoacoustic refrigerator via the resonant tube 17, driving its internal thermoacoustic oscillations and thermodynamic processes, generating a cooling effect at the cold-end heat exchanger 7, and completing the refrigeration cycle.

[0043] The magnetic screw-driven thermoacoustic refrigeration system provided in this embodiment of the invention uses a rotary motor 3 as a power source and utilizes the non-contact magnetic field coupling between the rotor permanent magnet 14 on the magnetic screw shaft 12 and the mover permanent magnet 13 on the compression piston 11 to efficiently convert rotational motion into reciprocating linear motion of the compression piston 11 to generate acoustic power, thereby driving the thermoacoustic refrigerator to produce a cooling effect. Thus, by using the rotary motor 3 and the magnetic coupling transmission mechanism to replace the linear compressor, the engineering challenges faced by existing electrically driven thermoacoustic refrigerators in high-precision linear support, gap sealing, magnetic circuit design, and vibration suppression are avoided, reducing the system's manufacturing difficulty and production cost, and facilitating mass production. Simultaneously, due to the high power density of the rotary motor 3 and the high energy transfer efficiency of the magnetic coupling transmission mechanism, the low power density and large volume problems caused by the introduction of a thermoacoustic engine in existing thermally driven thermoacoustic refrigerators are avoided. This allows for the output of a large amount of acoustic power within a smaller volume, meeting the application requirements of refrigeration equipment for high cooling capacity density, and is beneficial for system miniaturization and integration.

[0044] It should be noted that in this invention, the rotary motor 3 and the compression piston 11 are driven by magnetic coupling. There is no hard mechanical contact within the system, no physical wear parts, and the need for lubrication is eliminated. Combined with the characteristic of the thermoacoustic refrigeration unit having no moving mechanical parts at the low-temperature end, the entire thermoacoustic refrigeration system possesses high operational reliability and a long service life. Furthermore, when it is necessary to increase the system's cooling power, only the output power of the rotary motor 3 needs to be increased accordingly and adapted to the magnetic lead screw drive mechanism. This eliminates the challenges of high-precision support and vibration suppression under high power conditions faced by existing linear compressors, thus providing excellent power expansion capabilities.

[0045] In one embodiment of the present invention, the compression piston 11 and the inner wall of the pressure-resistant housing 4 can be supported by a sliding fit, a gas bearing, or a magnetic levitation bearing, so that it can move freely back and forth along the axial direction while restricting its circumferential rotation.

[0046] The compression piston 11 can be made of a magnetically conductive material with a certain rigidity, such as silicon steel, amorphous alloy, pure iron, low carbon steel, etc.

[0047] In one embodiment of the present invention, such as Figure 1 and Figure 2 As shown, the compression piston 11 is a cylindrical structure with one end closed axially. The closed end of the compression piston 11 is away from the rotary motor 3, and the closed end of the compression piston 11 and the inner wall of the pressure-resistant housing 4 form a compression chamber 15. When the compression piston 11 reciprocates, the volume of the compression chamber 15 changes periodically, thereby generating alternating gas pressure fluctuations in the compression chamber 15.

[0048] The magnetic screw shaft 12 extends axially into the internal cavity of the compression piston 11. Since the compression piston 11 is a cylindrical structure with an internal space, the magnetic screw shaft 12 can freely extend into this space without mechanically contacting the compression piston 11.

[0049] For example, the compression piston 11 adopts a closed-end annular structure, and the moving permanent magnet 13 is disposed on the inner surface of the compression piston 11. The cross-section of the moving permanent magnet 13 is an annular structure, and its axial length is less than the axial length of the compression piston 11.

[0050] The magnetic screw shaft 12 is coaxially arranged with the compression piston 11. One end of the magnetic screw shaft 12 is connected to the motor shaft 6 of the rotary motor 3, and the other end of the magnetic screw shaft 12 extends into the internal cavity of the compression piston 11. The rotor permanent magnet 14 is sleeved on the magnetic screw shaft 12. The cross-section of the rotor permanent magnet 14 is a circular ring structure. The magnetic screw shaft 12 is made of a magnetically conductive material with a certain rigidity, such as silicon steel, amorphous alloy, pure iron, low carbon steel, etc.

[0051] Optionally, the maximum displacement of the compression piston 11 in reciprocating linear motion is a first dimension, and the closed end of the compression piston 11 has a second dimension between the end face of the magnetic lead screw shaft 12 near the magnetic lead screw shaft 12 and the end face of the magnetic lead screw shaft 12 away from the rotary motor 3, and the first dimension is smaller than the second dimension.

[0052] In one embodiment of the present invention, the pressure wave generating device further includes a reset mechanism located on the side of the compression piston 11 away from the rotary motor 3, for providing restoring force for the reciprocating linear motion of the compression piston 11.

[0053] like Figure 1 As shown, the reset mechanism includes a piston rod 10 and an elastic element 16. The piston rod 10 is connected to the side of the compression piston 11 away from the rotary motor 3. The first end of the elastic element 16 is disposed on the inner wall of the pressure-resistant housing 4, and the second end of the elastic element 16 is connected to the end of the piston rod 10 away from the compression piston 11. It is used to provide a restoring force for the reciprocating linear motion of the compression piston 11 to ensure that it can be reliably reset in each cycle.

[0054] In one embodiment of the present invention, the elastic element 16 can be a mechanical spring or a gas spring. When the compression piston 11 reciprocates under the action of magnetic coupling, the elastic element 16 provides a restoring force to the compression piston 11 through its own elastic deformation and recovery, enabling it to complete a stable periodic motion.

[0055] Optionally, to reduce frictional losses between the compression piston 11 and the pressure-resistant housing 4, the pressure wave generating device further includes a gas bearing or a magnetic levitation bearing, which is disposed between the compression piston 11 and the pressure-resistant housing 4.

[0056] In this embodiment, when the elastic element 16 is a gas spring, the compression piston 11 is supported within the pressure-resistant housing 4 by a gas bearing. Specifically, the compression piston 11 is supported by a gas bearing, and the compression piston 11 and the pressure-resistant housing 4 are sealed by a gap seal.

[0057] In one embodiment of the present invention, such as Figure 2 As shown, an air gap is provided between the mover permanent magnet 13 and the rotor permanent magnet 14. They are coaxially arranged and spaced apart to ensure non-contact magnetic coupling. The permanent magnet structure of the mover permanent magnet 13 and / or the rotor permanent magnet 14 can be any of the following: radial magnetization structure, axial magnetization structure, a combination of radial and axial magnetization, or a combination of oblique ring-type discrete permanent magnets. It should be noted that the mover permanent magnet 13 and the rotor permanent magnet 14 can use the same or compatible permanent magnet structures. Compatibility means that their magnetization methods and magnetic pole distributions are matched to ensure effective magnetic coupling.

[0058] As an optional implementation, the rotor permanent magnet 14 and the mover permanent magnet 13 adopt the same permanent magnet structure. For example, the permanent magnet can be radially magnetized, with the magnetization direction along the radial direction of the permanent magnet and the N pole and S pole alternating along the axial direction. Along the axial direction of the magnetic screw shaft 12, the permanent magnet is divided into multiple segments, with the magnetization direction of each segment alternating between radially inward and radially outward, forming alternating magnetic field polarity and distribution between adjacent axial segments. When the rotor permanent magnet 14 rotates, the alternating magnetic field interacts with the corresponding alternating magnetic field on the mover permanent magnet 13, generating continuous axial thrust, driving the compression piston 11 to reciprocate linearly.

[0059] As an optional implementation, the rotor permanent magnet 14 adopts a Halbach structure, combining radial and axial magnetization. By rationally arranging permanent magnet units with different magnetization directions, such as radially inward magnetization, axial magnetization, radially outward magnetization, and reverse axial magnetization, the magnetic field on one side is enhanced while the magnetic field on the other side is canceled out. The Halbach structure can obtain a stronger magnetic field strength on the air gap side, improving the magnetic coupling efficiency.

[0060] As an optional implementation, the rotor permanent magnet 14 adopts a combination of inclined ring-shaped discrete permanent magnets, which is composed of multiple inclined ring-shaped discrete permanent magnet units spliced ​​together circumferentially. Each discrete permanent magnet can be selected with different tilt angles such as 30°, 45°, and 60°. By adjusting the tilt angle, the sinusoidal distribution characteristics of the magnetic field are optimized, the fluctuation of magnetic drag torque is reduced, and the magnetic coupling transmission is made smoother. Alternatively, an integral circular ring permanent magnet structure can also be adopted, that is, a permanent magnet processed into a single circular ring shape.

[0061] In one embodiment of the present invention, the rotor permanent magnet 14 is axially distributed along the outer surface of the magnetic lead screw shaft 12 in a double helix pattern, with the N pole and S pole alternating axially; or, the mover permanent magnet 13 is axially distributed along the inner surface of the compression piston 11 in a double helix pattern, with the N pole and S pole alternating axially; or, both are axially distributed in a double helix pattern, with both N pole and S pole alternating axially. All three methods can achieve continuous and smooth transmission through magnetic coupling, reducing torque pulsation.

[0062] For example, both the rotor permanent magnet 14 and the mover permanent magnet 13 adopt a double helix pattern. The permanent magnets are distributed axially along the outer surface of the magnetic screw shaft 12 and the inner surface of the compression piston 11 in a double helix pattern. That is, the permanent magnets are wound around the surface of the magnetic screw shaft 12 and the inner surface of the compression piston 11 in a double helix pattern. The N pole and S pole are alternately arranged axially, which makes the magnetic coupling more continuous and smooth during rotation, reduces torque pulsation, and improves the stability of system operation.

[0063] As another alternative axial distribution method, an integral circular permanent magnet can be used with N poles and S poles alternately arranged along the axial direction. That is, the single circular permanent magnet is magnetized in segments along the axial direction to form a structure in which N pole segments and S pole segments are arranged alternately, which can also achieve effective magnetic coupling between the rotor permanent magnet 14 and the mover permanent magnet 13.

[0064] In one embodiment of the present invention, the gap between the rotor permanent magnet 14 and the mover permanent magnet 13 is 1 mm to 4 mm, that is, the width of the air gap (radial along the magnetic screw shaft 12) is 1 mm to 4 mm.

[0065] In one embodiment of the present invention, the rotor permanent magnet 14 and the mover permanent magnet 13 have unequal axial lengths, with the axial length of the rotor permanent magnet 14 being greater than that of the mover permanent magnet 13. The axial length of the rotor permanent magnet 14 is 1-3 times the axial length of the mover permanent magnet 13.

[0066] In one embodiment of the present invention, the radial thickness of the rotor permanent magnet 14 is consistent with the radial thickness of the mover permanent magnet 13.

[0067] In one embodiment of the present invention, the radial thickness of the rotor permanent magnet 14 and the radial thickness of the mover permanent magnet 13 are both between 5 and 10 times the air gap width, so as to maximize the air gap magnetic flux density while preventing magnetic circuit saturation.

[0068] In one embodiment of the present invention, the rotary motor 3 may be a permanent magnet synchronous motor, an asynchronous motor or other types of motor, and the specific form is not limited.

[0069] The cavity formed between the compression piston 11 and the rotary motor 3 constitutes the back cavity 5.

[0070] In one embodiment, an installation cavity is formed inside the pressure-resistant housing 4, and the rotary motor 3 can be disposed inside the pressure-resistant housing 4. At this time, the magnetic coupling transmission mechanism and the rotary motor 3 are located on opposite sides inside the pressure-resistant housing 4.

[0071] In another embodiment, the pressure-resistant housing 4 can be a cavity structure with one end open. The outer shell of the rotary motor 3 is connected to the open end of the pressure-resistant housing 4, and a seal is formed between the two to form a sealed mounting cavity.

[0072] In one embodiment of the present invention, the rotary motor 3 and the magnetic coupling transmission mechanism can also adopt an integrated structure. Specifically, the rotor of the rotary motor 3 can be directly fixed on the magnetic lead screw shaft 12, and the stator of the rotary motor 3 can be directly installed on the inner wall of the pressure-resistant housing 4, so that the rotary motor 3 and the magnetic coupling transmission mechanism share the magnetic lead screw shaft 12 and the pressure-resistant housing 4.

[0073] In one embodiment of the present invention, the mounting cavity of the pressure-resistant housing 4 is filled with a gaseous working medium, which is one or more combinations of nitrogen, helium, carbon dioxide, and argon.

[0074] In one embodiment of the present invention, such as Figure 1 As shown, the thermoacoustic heat exchange assembly includes a cold-end heat exchanger 7, a regenerator 8, and a room-temperature heat exchanger 9 connected in sequence. The cold-end heat exchanger 7, the regenerator 8, and the room-temperature heat exchanger 9 are all built into the resonant tube 17. The pressure wave generator is installed at one end of the resonant tube 17 near the cold-end heat exchanger 7. The compression chamber 15 is connected to the end of the resonant tube 17 near the cold-end heat exchanger 7, thereby transmitting the acoustic power generated by the compression chamber 15 to the side where the cold-end heat exchanger 7 is located.

[0075] Understandably, one end of the resonant tube 17 is closed, and the other end is open. The cold-end heat exchanger 7, the regenerator 8, and the room-temperature heat exchanger 9 are built into the resonant tube 17 along its axial direction. The room-temperature heat exchanger 9 is located at the closed end of the resonant tube 17, and the cold-end heat exchanger 7 is located at the open end of the resonant tube 17. One end of the pressure-resistant housing 4 of the pressure wave generator, forming the compression chamber 15, is connected to the open end of the resonant tube 17, and the end of the pressure-resistant housing 4 is also provided with an opening to achieve communication between the compression chamber 15 and the resonant tube 17.

[0076] In this embodiment, when the thermoacoustic refrigeration system is working, the rotary motor 3 is connected to an external power source, driving the magnetic lead screw shaft 12 and the rotor permanent magnet 14 to rotate. Magnetic coupling is formed between the rotor permanent magnet 14 and the moving permanent magnet 13, converting the rotational mechanical work of the magnetic lead screw shaft 12 into acoustic work generated by the reciprocating linear motion of the compression piston 11. This acoustic work is transmitted sequentially to the cold-end heat exchanger 7, the regenerator 8, and the room-temperature end heat exchanger 9 in the form of alternating gas pressure fluctuations. Simultaneously, as the alternating gas pressure fluctuations reciprocate within the regenerator 8, they compress and expand, transferring heat from the cold-end heat exchanger 7 to the room-temperature end heat exchanger 9, and finally dissipating it into the external environment. This results in a low temperature at the cold-end heat exchanger 7, achieving cooling of the object placed there. At the same time, the alternating gas pressure fluctuations exchange heat with the regenerator packing as they flow through the regenerator, pumping heat from the cold end to the hot end.

[0077] Based on the magnetic screw-driven thermoacoustic cooling system provided in any of the above embodiments, embodiments of the present invention also provide a magnetic screw-driven thermoacoustic cooling method, such as... Figure 3 As shown, the method includes the following steps: S1. Control the rotary motor to run at a preset speed to output rotational mechanical energy, which is used to drive the magnetic lead screw shaft and the rotor permanent magnet to rotate continuously.

[0078] S2. By utilizing the magnetic field coupling between the rotating rotor permanent magnet and the moving permanent magnet, the rotational mechanical energy of the rotor permanent magnet is converted into the reciprocating linear motion of the compression piston.

[0079] S3. The compression piston reciprocates linearly within the pressure-resistant housing, periodically compressing and expanding the working gas filling the compression chamber, converting mechanical energy into acoustic energy in the form of alternating gas pressure fluctuations.

[0080] S4. Acoustic power drives a thermoacoustic refrigerator to perform a refrigeration cycle via a resonant tube.

[0081] Understandably, the rotary motor 3 is controlled to operate at a preset speed to output rotational mechanical energy. This rotational mechanical energy is used to drive the magnetic lead screw shaft 12 and the rotor permanent magnet 14 mounted thereon to rotate continuously. Utilizing the magnetic field coupling between the rotating rotor permanent magnet 14 and the moving permanent magnet 13, and due to the air gap between them and their relative arrangement, the rotating magnetic field generated by the rotation of the rotor permanent magnet 14 passes through the air gap and acts on the moving permanent magnet 13, applying a rotational torque to it. The moving permanent magnet 13 is fixedly connected to the compression piston 11, and the compression piston 11 can only perform reciprocating linear motion along the axial direction. Since it cannot rotate circumferentially, the rotational torque is converted into axial thrust, which converts the rotational mechanical energy of the rotor permanent magnet 14 into the reciprocating linear motion of the compression piston 11. The compression piston 11 reciprocates linearly within the pressure-resistant housing 4, periodically compressing and expanding the working gas filled in the compression chamber 15, thereby converting mechanical energy into acoustic power in the form of alternating gas pressure fluctuations. This acoustic power is transmitted to the thermoacoustic refrigerator via the resonant tube 17 in the form of alternating gas pressure fluctuations, driving its internal thermoacoustic oscillations and thermodynamic processes, generating a cooling effect at the cold-end heat exchanger 7, and completing the refrigeration cycle.

[0082] In one embodiment of the present invention, step 200, controlling the rotary motor to operate at a preset speed, may specifically include the following steps: Step 210: Obtain the acoustic resonant frequency of the thermoacoustic refrigeration system.

[0083] Step 220: Determine the target matching speed based on the acoustic resonant frequency and the magnetic pole lead of the magnetic coupling transmission mechanism.

[0084] Step 230: Adjust the rotation speed of the rotary motor to the target matching speed.

[0085] Understandably, the acoustic resonant frequency of the thermoacoustic refrigeration system is obtained, and this frequency is determined by the structural parameters of the thermoacoustic refrigerator (such as the length of the resonant tube and the type of internal working gas). Based on the obtained acoustic resonant frequency and the magnetic pole lead of the magnetic coupling transmission mechanism, a target matching speed that matches the acoustic resonant frequency is determined. The magnetic pole lead refers to the periodic distance of the magnetic poles distributed axially between the rotor permanent magnet and the mover permanent magnet. The actual operating speed of the rotating motor is adjusted to this target matching speed, so that the frequency of the alternating gas pressure fluctuations generated by the compression piston matches the acoustic resonant frequency of the thermoacoustic refrigeration system, thereby enabling the entire thermoacoustic refrigeration system to reach an acoustic resonant operating state. In this resonant state, the phase relationship between the pressure wave and the mass flow inside the system is optimized, minimizing the dissipation of acoustic power during transmission and improving the efficiency of thermoacoustic refrigeration.

[0086] Example 2 The difference between this embodiment and Embodiment 1 is that: Figure 4As shown, the thermoacoustic heat exchange assembly includes a room temperature heat exchanger 9, a regenerator 8, a cold end heat exchanger 7, a thermal buffer tube 1, and a sub-room temperature heat exchanger 2 connected in sequence. The thermoacoustic refrigerator also includes a feedback tube 18. The feedback tube 18 is connected between the sub-room temperature heat exchanger 2 and the room temperature heat exchanger 9 to form an acoustic loop structure. The first end of the resonant tube 17 is connected to the compression chamber 15, and the second end of the resonant tube 17 is connected to the feedback tube 18.

[0087] In this embodiment, when the thermoacoustic refrigeration system is working, the rotary motor 3 is connected to an external power source, driving the magnetic lead screw shaft 12 and the rotor permanent magnet 14 to rotate. The relative motion between the rotor permanent magnet 14 and the moving permanent magnet 13 converts the rotational mechanical work of the magnetic lead screw shaft 12 into acoustic work generated by the reciprocating linear motion of the compression piston 11 through the magnetic force of the permanent magnet. The acoustic work generated by the compression piston 11 is transmitted sequentially to the feedback tube 18, the room temperature end heat exchanger 9, the regenerator 8, the cold end heat exchanger 7, the thermal buffer tube 1, and the sub-room temperature end heat exchanger 2 in the form of alternating gas pressure fluctuations. While the alternating gas pressure fluctuations reciprocate within the regenerator 8, they also transfer heat from the cold end heat exchanger 7 to the room temperature end heat exchanger 9 through compression and expansion, and finally dissipate it to the external environment through the room temperature end heat exchanger 9, thereby achieving a low temperature at the cold end heat exchanger 7 and cooling the object placed at the cold end heat exchanger 7. Meanwhile, pressure fluctuations exchange heat with the regenerator packing as they flow through the regenerator, pumping heat from the cold end to the hot end. It should be noted that, compared with Embodiment 1, the sound field in the regenerator in this embodiment is dominated by traveling wave sound field, that is, the phase difference between pressure fluctuation and volume flow fluctuation is close to zero. Therefore, the thermoacoustic refrigerator in this embodiment has higher cooling efficiency.

[0088] Example 3 The difference between this embodiment and embodiment one is that: the thermoacoustic refrigeration basic unit 01 has at least three thermoacoustic refrigerators, and the thermoacoustic refrigerators of two adjacent thermoacoustic refrigeration basic units are connected through a resonant tube 17 to form a traveling wave thermoacoustic loop; the thermoacoustic heat exchange assembly includes a sub-room temperature end heat exchanger 2, a heat buffer tube 1, a cold end heat exchanger 7, a regenerator 8, and a room temperature end heat exchanger 9 connected in sequence.

[0089] For example, such as Figure 5 and Figure 6 As shown, the thermoacoustic refrigeration system includes three basic thermoacoustic refrigeration units 01 (i.e., a three-stage thermoacoustic refrigeration unit). Each basic thermoacoustic refrigeration unit includes a thermoacoustic refrigerator, which has a sub-room temperature end heat exchanger 2, a heat buffer tube 1, a cold end heat exchanger 7, a regenerator 8, and a room temperature end heat exchanger 9 connected in sequence. A pressure wave generator is connected to the first end of the resonant tube 17, and the compression chamber 15 is connected to the resonant tube 17; the second end of the resonant tube 17 is connected to the next adjacent basic thermoacoustic refrigeration unit.

[0090] In this embodiment, each thermoacoustic refrigeration basic unit is equipped with two opposing pressure wave generators. The two pressure wave generators are coaxial and opposite to each other, and their compression chambers 15 are connected. The two pressure wave generators are connected to the resonant tube 17 of the thermoacoustic refrigeration basic unit and are located on the side closer to the room temperature heat exchanger 2 of that stage. Alternatively, the two opposing pressure wave generators can also bypass the resonant tube 17 of the previous stage thermoacoustic refrigeration basic unit and be located on the side closer to the room temperature heat exchanger 9 of that stage.

[0091] In this embodiment, when the thermoacoustic refrigeration system is working, the rotary motor 3 in each stage of the thermoacoustic refrigeration basic unit drives the magnetic lead screw shaft 12 and the rotor permanent magnet 14 to rotate. Through magnetic coupling, the rotational mechanical work is converted into acoustic work generated by the reciprocating linear motion of the compression piston 11. In the first stage of the thermoacoustic refrigeration basic unit, the acoustic work generated by the pressure wave generator is transmitted in the form of pressure waves through the resonant tube 17 to the room temperature end heat exchanger 9, the regenerator 8, the cold end heat exchanger 7, the thermal buffer tube 1, and the sub-room temperature end heat exchanger 2. While the pressure wave reciprocates in the regenerator 8, it transfers the heat at the cold end heat exchanger 7 to the room temperature end heat exchanger 9 through the regenerator 8 via compression and expansion, and finally dissipates it to the external environment through the room temperature end heat exchanger 9, thereby achieving a low temperature at the cold end heat exchanger 7. The remaining acoustic power after passing through the regenerator 8 flows sequentially through the cold-end heat exchanger 7, the thermal buffer tube 1, and the sub-room temperature-end heat exchanger 2, before being output to the resonant tube 17 of the second-stage thermoacoustic refrigeration basic unit. There, it merges with the acoustic power output from the second-stage pressure wave generator and enters the second-stage room temperature-end heat exchanger 9. Similarly, the remaining acoustic power from the second stage is transferred to the third stage, and the remaining acoustic power from the third stage returns to the first stage through a loop structure, achieving the progressive transfer and recycling of acoustic power. This cycle constitutes a loop-type traveling wave thermoacoustic refrigeration system driven by the pressure wave generator.

[0092] It should be noted that, compared with Embodiment 1, in the thermoacoustic refrigerator of this embodiment, the sound field in the regenerator 8 is dominated by a traveling wave sound field (that is, the phase difference between pressure fluctuation and volume flow fluctuation is close to zero). Therefore, the thermoacoustic refrigerator of this embodiment has higher cooling efficiency and a larger overall cooling capacity.

[0093] Example 4 The difference between this embodiment and Embodiment 3 is that each thermoacoustic refrigeration basic unit includes a pressure wave generator.

[0094] Specifically, three thermoacoustic refrigeration basic units are connected end-to-end to form a traveling wave thermoacoustic loop, with each unit equipped with a pressure wave generator. This pressure wave generator is connected to the resonant tube 17 of its unit and located near the sub-room temperature heat exchanger 2, or it is bypassed and connected to the resonant tube 17 of the previous stage thermoacoustic refrigeration basic unit and located near the room temperature heat exchanger 9 of that stage. During system operation, the acoustic power of each stage is provided solely by the pressure wave generator of that stage, and it combines with the remaining acoustic power transmitted from the previous stage to jointly drive the thermoacoustic refrigerator of that stage for thermoacoustic conversion. Compared to Embodiment 3, this embodiment reduces the number of pressure wave generators, which helps to reduce system cost and structural complexity, making it suitable for applications with medium cooling capacity requirements.

[0095] Finally, it should be noted that the above embodiments are only for illustrating the present invention and not for limiting the present invention. Although the present invention has been described in detail with reference to the embodiments, those skilled in the art should understand that various combinations, modifications, or equivalent substitutions of the technical solutions of the present invention do not depart from the spirit and scope of the technical solutions of the present invention and should be covered within the scope of the claims of the present invention.

Claims

1. A thermoacoustic cooling system driven by a magnetic lead screw, characterized in that, It includes at least one thermoacoustic refrigeration basic unit, the thermoacoustic refrigeration basic unit comprising: A pressure wave generating device includes a pressure-resistant housing, a rotary motor, and a magnetic coupling transmission mechanism disposed within the pressure-resistant housing. The magnetic coupling transmission mechanism includes a magnetic lead screw shaft, a moving permanent magnet, a compression piston, and a rotor permanent magnet disposed on the magnetic lead screw shaft. The magnetic lead screw shaft is drivenly connected to the output end of the rotary motor. The compression piston is reciprocating linearly within the pressure-resistant housing. The moving permanent magnet is connected to the compression piston and arranged at a distance from the rotor permanent magnet. A compression cavity is formed between the compression piston and the pressure-resistant housing. Thermoacoustic refrigerator, including thermoacoustic heat exchange components for performing thermoacoustic energy conversion; A resonant tube, which is connected to the compression cavity and the thermoacoustic refrigerator respectively and forms acoustic coupling; The rotary motor drives the magnetic lead screw shaft and the rotor permanent magnet to rotate. Through the magnetic field coupling between the rotor permanent magnet and the moving permanent magnet, the rotational mechanical energy of the rotary motor is converted into the reciprocating linear motion of the compression piston to generate acoustic power. The acoustic power drives the thermoacoustic refrigerator to perform a refrigeration cycle in the form of alternating gas pressure fluctuations via the resonant tube.

2. The magnetic screw-driven thermoacoustic cooling system according to claim 1, characterized in that, The pressure wave generating device further includes: A piston rod, which is connected to the side of the compression piston away from the rotary motor; An elastic element has a first end disposed on the inner wall of the pressure-resistant housing and a second end connected to the end of the piston rod away from the compression piston. The elastic element is used to provide a restoring force to the compression piston for reciprocating linear motion.

3. The magnetic screw-driven thermoacoustic cooling system according to claim 2, characterized in that, The pressure wave generating device further includes: A gas bearing or a magnetic levitation bearing is disposed between the compression piston and the pressure-resistant housing.

4. The magnetic screw-driven thermoacoustic cooling system according to claim 1, characterized in that, The gap between the rotor permanent magnet and the mover permanent magnet is 1mm to 4mm.

5. The magnetic screw-driven thermoacoustic cooling system according to any one of claims 1 to 4, characterized in that, The thermoacoustic heat exchange assembly includes a cold-end heat exchanger, a regenerator, and a room-temperature heat exchanger connected in sequence. The cold-end heat exchanger, the regenerator, and the room-temperature heat exchanger are all built into the resonant tube, and the compression chamber is connected to the end of the resonant tube near the cold-end heat exchanger.

6. The magnetic screw-driven thermoacoustic cooling system according to any one of claims 1 to 4, characterized in that, The thermoacoustic heat exchange assembly includes a room temperature heat exchanger, a regenerator, a cold temperature heat exchanger, a thermal buffer tube, and a sub-room temperature heat exchanger connected in sequence; the thermoacoustic refrigerator also includes a feedback tube, which is connected between the sub-room temperature heat exchanger and the room temperature heat exchanger to form an acoustic loop structure; the first end of the resonant tube is connected to the compression chamber, and the second end of the resonant tube is connected to the feedback tube.

7. The thermoacoustic cooling system driven by a magnetic lead screw according to claim 1, characterized in that, The thermoacoustic refrigeration basic unit has at least three units, and the thermoacoustic refrigerators of two adjacent thermoacoustic refrigeration basic units are connected through the resonant tube to form a traveling wave thermoacoustic loop. Each thermoacoustic refrigerator contains a thermoacoustic heat exchange component comprising a secondary room temperature end heat exchanger, a heat buffer tube, a cold end heat exchanger, a regenerator, and a room temperature end heat exchanger connected in sequence. The pressure wave generating device is connected to the resonant tube, and the compression chamber is connected to the resonant tube.

8. The magnetic screw-driven thermoacoustic cooling system according to claim 1, characterized in that, Each of the thermoacoustic refrigeration basic units includes two pressure wave generating devices, which are coaxial and arranged opposite to each other, and the compression chambers of the two pressure wave generating devices are connected.

9. A thermoacoustic cooling method driven by a magnetic lead screw, characterized in that, The method, applied to a magnetically driven thermoacoustic refrigeration system as described in any one of claims 1 to 8, comprises: The rotary motor is controlled to operate at a preset speed to output rotational mechanical energy, which is used to drive the magnetic lead screw shaft and the rotor permanent magnet to rotate continuously. By utilizing the magnetic field coupling between the rotating rotor permanent magnet and the moving permanent magnet, the rotational mechanical energy of the rotor permanent magnet is converted into the reciprocating linear motion of the compression piston; The compression piston reciprocates linearly within the pressure-resistant housing, periodically compressing and expanding the working gas filling the compression chamber, converting mechanical energy into acoustic energy in the form of alternating gas pressure fluctuations. The acoustic power drives the thermoacoustic refrigerator to perform a refrigeration cycle via the resonant tube.

10. The thermoacoustic cooling method driven by a magnetic lead screw according to claim 9, characterized in that, Controlling the rotary motor to operate at a preset speed includes: Obtain the acoustic resonant frequency of the thermoacoustic refrigeration system; The target matching speed is determined based on the acoustic resonant frequency and the magnetic pole lead of the magnetic coupling transmission mechanism; Adjust the rotational speed of the rotary motor to the target matching speed.

Images