A forced circulation cooling device for magnetic couplers

Abstract

This application relates to the field of magnetic coupler technology, and more particularly to a forced circulation cooling device for magnetic couplers, comprising a driver, a flange, a supporting water jacket, an outer magnetic steel body, an inner magnetic steel body, and a sealing cover. A booster turbine is disposed on the bottom end face of the outer magnetic steel body. By placing the booster turbine on the bottom end face of the outer magnetic steel body, the booster turbine rotates synchronously with the outer magnetic steel body. The booster turbine is driven by the rotational power of the outer magnetic steel body itself, eliminating the need for an additional drive device, thus simplifying the overall structure of the cooling device and reducing its complexity and manufacturing cost. The turbine blades are configured as streamlined curved surfaces facing the direction of rotation. When the booster turbine rotates with the outer magnetic steel body, the streamlined curved blades can more smoothly compress the cooling water in front, enhancing the driving effect on the cooling water and effectively increasing the flow rate and velocity of the cooling water entering the narrow gap between the outer magnetic steel body and the sealing cover, thereby extending its service life.

Description

Technical Field

[0001] This utility model relates to the field of magnetic coupler technology, and in particular to a forced circulation cooling device for magnetic couplers. Background Technology

[0002] As an important static sealing transmission component in stirred reaction equipment, the magnetic coupler effectively solves the leakage problems of traditional mechanical seals and packing seals due to its non-contact magnetic torque transmission characteristics. It is widely used in hazardous working conditions such as high temperature, high pressure, toxic, flammable and explosive environments.

[0003] like Figure 1 As shown, this is a common magnetic coupler on the market. During its operation, the driver 1 drives the outer magnet 4 to rotate through a transmission pair consisting of a flange 2 and bearing assemblies. The outer magnet 4 transfers the kinetic energy of the driver 1 to the inner magnet 5 through magnetic force. The inner magnet 5 then links the stirring shaft and the stirrer, completing the rotational motion of the stirrer and realizing the power transmission of the magnetic coupler. To ensure efficient transmission of magnetic torque, the distance between the outer magnet 4 and the inner magnet 5 needs to be as small as possible. In addition, a sealing cover 6 is required between them to isolate the inner and outer spaces, making the gap between the outer magnet 4 and the sealing cover 6 only 1-2mm. During the magnetic coupling power transmission process, the magnetic lines of force cutting the sealing cover 6 will cause it to heat up. Since magnetic materials are sensitive to temperature changes, excessively high temperatures will reduce the material strength and weaken the magnetism of the inner and outer magnets, greatly affecting the working efficiency and service life of the magnetic coupler.

[0004] To address the heat generation issue, current solutions typically involve immersing the outer magnet 4 and the sealing cover 6 in a supporting water jacket 3 containing coolant, relying on the coolant's self-circulation to remove heat. However, due to the very small gap between the outer magnet 4 and the inner magnet 5, cooling water passage is difficult and the flow rate is low. When the outer magnet 4 rotates, the cooling water passing through the gap changes to a circumferential flow around the sealing cover, further hindering the entry of subsequent cooling water. Consequently, the cooling effect is not ideal, and the higher the rotational speed, the worse the cooling effect becomes, thus restricting the development of magnetic couplers towards larger sizes, higher torque, and higher rotational speeds. Summary of the Invention

[0005] To address the above problems, this application provides a forced circulation cooling device for a magnetic coupler, comprising a driver, a flange, a supporting water jacket, an outer magnetic steel body, an inner magnetic steel body, and a sealing cover. A booster turbine is provided on the bottom end face of the outer magnetic steel body, and the booster turbine rotates synchronously with the outer magnetic steel body. The turbine blades of the booster turbine are streamlined curved surfaces facing the direction of rotation.

[0006] In one embodiment, a centrifugal impeller is axially mounted on the flange, and centrifugal blades are evenly distributed around the circumference of the centrifugal impeller; an axially penetrating cooling water rising channel is formed between the flange and the centrifugal impeller.

[0007] In one embodiment, the centrifugal blades divide the centrifugal impeller into multiple centrifugal chambers, and each centrifugal chamber is provided with a cooling water rising channel at its bottom. The centrifugal blades of the centrifugal impeller are streamlined curved surfaces facing away from the direction of rotation.

[0008] In one embodiment, the cooling water rising channel includes: a first flow channel hole formed on the flange face of the flange, arranged in a ring array; and a second flow channel hole formed on the centrifugal impeller, wherein the first flow channel hole and the second flow channel hole are arranged in a one-to-one correspondence.

[0009] In one embodiment, the centrifugal impeller is fixedly mounted on the flange, and the flange is fixedly connected to the outer magnet body.

[0010] In one embodiment, a water seal is installed at the bottom inner side of the turbocharger, and the water seal forms a dynamic seal structure with radial interference fit with the outer surface of the sealing cover.

[0011] In one embodiment, the turbine blades are evenly distributed along the circumference of the booster turbine, and the extension direction of the turbine blade surface forms an acute angle with the rotation direction.

[0012] In one embodiment, the supporting water jacket is provided with a cooling water inlet, a cooling water outlet and a cooling water overflow port; the cooling water inlet is located at the bottom of the supporting water jacket, and the cooling water outlet and the overflow port are located at the top of the supporting water jacket.

[0013] In one embodiment, the booster turbine is fixedly mounted on the outer magnet body, and an annular narrow gap is formed between the inner flow channel of the booster turbine and the outer surface of the sealing cover body, the annular narrow gap corresponding to the gap between the outer magnet body and the sealing cover body.

[0014] The beneficial effects of this utility model are as follows:

[0015] This application discloses a forced circulation cooling device for a magnetic coupler. A booster turbine is installed on the bottom end face of the outer magnet, rotating synchronously with the outer magnet. The booster turbine is driven by the rotational power of the outer magnet itself, eliminating the need for an additional drive unit. This simplifies the overall structure of the cooling device and reduces its complexity and manufacturing cost. The turbine blades are designed as streamlined curved surfaces facing the direction of rotation. As the booster turbine rotates with the outer magnet, the streamlined blades can more smoothly compress the cooling water in front, enhancing the driving effect on the cooling water. This effectively increases the flow rate and velocity of the cooling water entering the narrow gap between the outer magnet and the sealing cover, accelerating the circulation speed of the cooling water between the outer magnet and the sealing cover. This ensures that the heat generated by the magnetic lines of force cutting in the sealing cover is promptly dissipated, preventing the outer and inner magnets from weakening due to excessive temperature. This ensures that the magnets operate within a suitable temperature range, thereby improving the working efficiency of the magnetic coupler, extending its service life, and better adapting to the development needs of larger, higher torque, and higher speed couplings. Attached Figure Description

[0016] Figure 1 This is a cross-sectional view of a magnetic coupler in the prior art;

[0017] Figure 2 This is a cross-sectional view of the present invention;

[0018] Figure 3 for Figure 2 Enlarged view at point A;

[0019] Figure 4 This is a schematic diagram of a turbocharger structure;

[0020] Figure 5 Top view of the supercharger turbine;

[0021] Figure 6 This is a schematic diagram of a centrifugal impeller structure;

[0022] Figure 7 Comparison of flow field simulation cloud maps at 100 rpm;

[0023] Figure 8 Comparison of flow field simulation cloud maps at 200 rpm;

[0024] Figure 9 This is a trace diagram;

[0025] Explanation of symbols in the diagram:

[0026] 1. Driver;

[0027] 2. Flange;

[0028] 3. Supporting water jacket; 31. Cooling water inlet; 32. Cooling water outlet; 33. Cooling water overflow outlet;

[0029] 4. External magnetic steel body;

[0030] 5. Internal magnetic steel body;

[0031] 6. Sealed cover;

[0032] 7. Supercharger turbine; 71. Turbine blades;

[0033] 8. Centrifugal impeller; 81. Centrifugal blades; 82. Centrifugal chamber; 83. First flow channel orifice; 84. Second flow channel orifice;

[0034] 9. Water seal. Detailed Implementation

[0035] To make the technical problems, technical solutions, and beneficial effects to be solved by this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and are not intended to limit the scope of this application.

[0036] It should be noted that 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 technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0037] like Figure 2-5 As shown, a forced circulation cooling device for a magnetic coupler includes a driver 1, a flange 2, a supporting water jacket 3, an outer magnetic steel body 4, an inner magnetic steel body 5, and a sealing cover 6. A booster turbine 7 is provided on the bottom end face of the outer magnetic steel body 4. The booster turbine 7 rotates synchronously with the outer magnetic steel body 4. The turbine blades 71 of the booster turbine 7 are streamlined curved surfaces facing the direction of rotation.

[0038] Specifically, this device includes a driver 1, a flange 2, a supporting water jacket 3, an outer magnetic steel body 4, an inner magnetic steel body 5, and a sealing cover 6. The sealing cover 6 is located between the outer magnetic steel body 4 and the inner magnetic steel body 5, serving to isolate the inner and outer spaces. The driver 1 is connected to the outer magnetic steel body 4 through the flange 2 and drives the outer magnetic steel body 4 to rotate. The outer magnetic steel body 4 is assembled inside the supporting water jacket 3, and a booster turbine 7 is provided on its bottom end face. The booster turbine 7 is fixedly connected to the outer magnetic steel body 4 and rotates synchronously with the outer magnetic steel body 4. The booster turbine 7 is circumferentially equipped with turbine blades 71, which are distributed in a streamlined curved surface facing the direction of rotation. Its working principle is based on the power transmission process of a magnetic coupler. When the driver 1 is running, it drives the outer magnetic steel body 4 to rotate through the driver 1 and the flange 2. At this time, the booster turbine 7, which rotates synchronously with the outer magnetic steel body 4, also rotates. Because the turbine blade 71 is a streamlined curved surface facing the direction of rotation, the cooling water in front of the turbine blade 71 is compressed during rotation and moves along the streamlined curved surface of the blade to the rear and upward, thus forming a flow tendency towards the inside of the booster turbine 7. This allows the cooling water to enter the gap between the outer magnet 4 and the sealing cover 6 more efficiently and participate in the cooling cycle. In this application, by setting the booster turbine 7 on the bottom end face of the outer magnet 4, and the booster turbine 7 rotating synchronously with the outer magnet 4, the booster turbine is driven by the rotational power of the outer magnet 4 itself. This eliminates the need for an additional drive device, simplifying the overall structure of the cooling device and reducing the complexity and manufacturing cost of the equipment. The turbine blades 71 are designed as streamlined curved surfaces facing the direction of rotation. When the supercharger turbine 7 rotates with the outer magnet 4, the streamlined curved blades can more smoothly squeeze the cooling water in front, enhancing the driving effect on the cooling water. This effectively increases the flow rate and volume of cooling water entering the narrow gap between the outer magnet 4 and the sealing cover 6, accelerating the circulation speed of the cooling water between the outer magnet 4 and the sealing cover 6. This allows the heat generated by the magnetic lines of force cutting in the sealing cover to be carried away in time, preventing the outer magnet 4 and inner magnet 5 from reducing their strength and weakening their magnetism due to excessive temperature. This ensures that the magnets work within a suitable temperature range, thereby improving the working efficiency of the magnetic coupler, extending its service life, and better adapting to the development needs of large-scale, high-torque, and high-speed applications.

[0039] like Figure 6 As shown, a centrifugal impeller 8 is axially mounted on the flange 2, and centrifugal blades 81 are evenly distributed around the circumference of the centrifugal impeller 8; an axially penetrating cooling water rising channel is formed between the flange 2 and the centrifugal impeller 8.

[0040] Specifically, a centrifugal impeller 8 with circumferentially distributed centrifugal blades 81 is axially mounted on flange 2, and an axially connected cooling water rising channel is formed between flange 2 and centrifugal impeller 8. When centrifugal impeller 8 rotates synchronously with outer magnet 4, centrifugal blades 81 will generate centrifugal force on the surrounding cooling water during rotation. Combined with the axially connected cooling water rising channel, it can effectively form an upward suction force, accelerating the upward flow of cooling water between outer magnet 4 and sealing cover 6. At the same time, the circumferentially distributed design of centrifugal blades 81 can make the cooling water uniformly stressed, avoiding local water flow turbulence. Combined with the pushing action of turbocharger 7 on cooling water, a dual power of "push and suction" is formed, which greatly improves the flow rate and volume of cooling water in narrow gaps and rising channels, solving the problem that cooling water in the original cooling system easily forms a circumferential flow that hinders subsequent water intake.

[0041] like Figure 6 As shown, the centrifugal blades 81 divide the centrifugal impeller 8 into multiple centrifugal chambers 82, and each centrifugal chamber 82 has a corresponding cooling water rising channel at its bottom. The centrifugal blades 81 of the centrifugal impeller 8 are streamlined curved surfaces facing away from the direction of rotation.

[0042] Specifically, the centrifugal blades 81 divide the centrifugal impeller 8 into multiple centrifugal chambers 82. Each centrifugal chamber 82 has a corresponding cooling water rising channel at its bottom. The centrifugal blades 81 are streamlined curved surfaces facing away from the direction of rotation. The one-to-one correspondence between the multiple centrifugal chambers 82 and the corresponding cooling water rising channels allows the cooling water to enter the chambers in an orderly manner from each channel, avoiding mutual interference of water flow during the rising process and ensuring the stability of the water flow. When the centrifugal impeller 8 rotates with the outer magnet 4, the cooling water in front of the blades will move smoothly outward and backward along the streamlined curved surface of the blades under the combined action of centrifugal force and the curved surface of the blades. This can effectively reduce water flow resistance and at the same time reduce the pressure in each centrifugal chamber 82 more evenly, forming a stronger suction force.

[0043] like Figure 6 As shown, the cooling water rising channel includes: a first flow channel hole 83 opened on the flange face of the flange 2, which is distributed in a ring array; and a second flow channel hole 84 opened on the centrifugal impeller 8, wherein the first flow channel hole 83 and the second flow channel hole 84 are arranged in a one-to-one correspondence.

[0044] Specifically, the cooling water rising channel consists of a first flow channel hole 83 arranged in a ring array on the flange face of flange 2, and a second flow channel hole 84 arranged on centrifugal impeller 8 corresponding to the first flow channel hole 83. The ring array of the first flow channel hole 83 allows the cooling water to enter the channel more evenly, avoiding local water concentration or insufficient water intake. The one-to-one correspondence between the first flow channel hole 83 and the second flow channel hole 84 ensures the continuity of the flow path of the cooling water during the rising process, reduces the resistance loss caused by water flow turning or diversion, and allows the cooling water to enter the centrifugal chamber 82 of centrifugal impeller 8 more smoothly from flange 2.

[0045] like Figure 2 , 3 As shown, the centrifugal impeller 8 is fixedly installed on the flange 2, and the flange 2 is fixedly connected to the outer magnet body 4.

[0046] Specifically, the axial length of flange 2 is increased to accommodate centrifugal impeller 8. Centrifugal impeller 8 is fixedly mounted on flange 2 using circumferentially distributed bolt assemblies, and flange 2 is fixedly connected to outer magnet body 4. This ensures that centrifugal impeller 8, flange 2, and outer magnet body 4 form a stable whole, achieving synchronous rotation of the three during equipment operation. This avoids relative movement caused by loose connections, ensuring the stability and consistency of centrifugal impeller 8's rotation. Synchronous rotation allows the centrifugal force of centrifugal impeller 8 to precisely match the rotation rhythm of outer magnet body 4. Combined with the booster turbine's push on cooling water, a stable and continuous "push and suction" dual force can be formed, effectively avoiding water flow turbulence caused by differences in rotational speed between components, and further improving the flow efficiency of cooling water in the flow channel orifice and narrow gap.

[0047] like Figure 2 As shown, a water seal 9 is installed at the bottom inner side of the turbocharger 7, and the water seal 9 forms a dynamic sealing structure with radial interference fit with the outer surface of the sealing cover 6.

[0048] Specifically, the water seal 9 is an annular wear-resistant soft rubber component, interference-fitted onto the outer surface of the sealing cover 6, with at least one annular sealing protrusion on its inner ring. This radial interference fit dynamic seal structure ensures that the water seal 9 and the sealing cover 6 maintain tight contact as the booster turbine 7 rotates with the outer magnet 4, effectively blocking the downward flow path of the cooling water. This forces the cooling water to flow only inwards and upwards under the push of the booster turbine 7, concentrating it into the narrow gap between the outer magnet 4 and the sealing cover 6. This prevents cooling water loss due to leakage and improves the utilization efficiency of the cooling water. Simultaneously, this dynamic seal structure can adapt to the relative rotational motion of both components, ensuring the reliability of the seal while reducing obstruction to equipment operation. This further increases the flow rate and velocity of the cooling water within the narrow gap, enhancing the cooling effect on the sealing cover 6.

[0049] like Figure 4, 5 As shown, the turbine blades 71 are evenly distributed around the circumference of the supercharger turbine 7, and the extension direction of the curved surface of the turbine blades 71 forms an acute angle with the rotation direction.

[0050] Specifically, the turbine blades 71 are evenly distributed around the circumference of the supercharger turbine 7, and the direction of their curved extension forms an acute angle with the direction of rotation. The evenly distributed turbine blades 71 can ensure that the cooling water is subjected to uniform thrust when the supercharger turbine 7 rotates, avoiding flow turbulence caused by uneven force on local water flow, and ensuring the uniformity of cooling water entering the narrow gap between the outer magnet body 4 and the sealing cover 6. The acute angle between the direction of the curved extension and the direction of rotation allows the blades to more efficiently squeeze the cooling water in front during rotation. The curved extension along the acute angle direction can guide the water flow to flow inward and upward, reduce the energy loss caused by water flow impact, enhance the guiding and pushing effect on the cooling water, and further improve the flow rate and flow of the cooling water in the narrow gap.

[0051] like Figure 2 As shown, the supporting water jacket 3 is provided with a cooling water inlet 31, a cooling water outlet 32 ​​and a cooling water overflow port 33; the cooling water inlet 31 is located at the bottom of the supporting water jacket 3, and the cooling water outlet 32 ​​and the overflow port 33 are located at the top of the supporting water jacket 3.

[0052] Specifically, the cooling water inlet 31 on the supporting water jacket 3 is located at the bottom, while the cooling water outlet 32 ​​and overflow port 33 are located at the top. The cooling water inlet 31 at the bottom allows cooling water to enter from the lower part of the supporting water jacket 3, ensuring that the cooling water can fully cover the surfaces of the outer magnet 4 and the sealing cover 6. The cooling water outlet 32 ​​and overflow port 33 at the top provide a reasonable discharge path for the cooling water, ensuring that the cooling water after absorbing heat can be discharged in a timely manner, and that the overflow port 33 can also play a pressure relief role when the cooling water flow is too large, preventing excessive pressure inside the supporting water jacket 3 from affecting the operation of the equipment. The bottom-in, top-out layout, together with the function of the booster turbine 7 and the centrifugal impeller 8, forms a complete and efficient cooling cycle, allowing the cooling water to fully contact the parts to be cooled during the flow process, maximizing the removal of heat generated by the magnetic lines of force cutting in the sealing cover 6, and improving cooling efficiency.

[0053] like Figure 2 , 3 As shown, the supercharger turbine 7 is fixedly mounted on the outer magnet body 4. An annular narrow gap is formed between the inner flow channel of the supercharger turbine 7 and the outer surface of the sealing cover 6. The annular narrow gap corresponds to the gap between the outer magnet body 4 and the sealing cover 6.

[0054] Specifically, the gap width is 1-3mm. The rotation of the booster turbine 7 is used to force cooling water into the gap between the sealing cover 6 and the outer magnet 4. The booster turbine 7 is fixedly installed on the outer magnet 4, and the annular narrow gap formed by its inner flow channel and the outer surface of the sealing cover 6 corresponds to the gap between the outer magnet 4 and the sealing cover 6. The fixed installation ensures that the booster turbine 7 rotates synchronously with the outer magnet 4, so that the turbine blades 71 can stably apply thrust to the cooling water; and the correspondence between the annular narrow gap and the gap between the outer magnet 4 and the sealing cover allows the cooling water to enter the core gap area that needs to be cooled precisely and continuously under the drive of the booster turbine, reducing water flow dispersion.

[0055] This application discloses a forced circulation cooling device for a magnetic coupler. Its working principle is based on the power transmission process of the magnetic coupler. When the driver 1 operates, it drives the outer magnetic steel body 4 to rotate via the driver 1 and flange 2. Simultaneously, the booster turbine 7, which rotates synchronously with the outer magnetic steel body 4, also rotates. Since the turbine blades 71 are streamlined curved surfaces facing the direction of rotation, the cooling water in front of the turbine blades 71 is compressed during rotation and moves along the streamlined curved surface of the blades upwards and backwards, thus forming a flow tendency towards the inside of the booster turbine 7. This allows the cooling water to enter the gap between the outer magnetic steel body 4 and the sealing cover 6 more efficiently, participating in the cooling cycle. In this application, by setting the booster turbine 7 on the bottom end face of the outer magnetic steel body 4, and having the booster turbine 7 rotate synchronously with the outer magnetic steel body 4, the booster turbine is driven by the rotational power of the outer magnetic steel body 4 itself. This eliminates the need for an additional drive device, simplifying the overall structure of the cooling device and reducing the complexity and manufacturing cost of the equipment. The turbine blades 71 are designed as streamlined curved surfaces facing the direction of rotation. When the supercharger turbine 7 rotates with the outer magnet 4, the streamlined curved blades can more smoothly squeeze the cooling water in front, enhancing the driving effect on the cooling water. This effectively increases the flow rate and volume of cooling water entering the narrow gap between the outer magnet 4 and the sealing cover 6, accelerating the circulation speed of the cooling water between the outer magnet 4 and the sealing cover 6. This allows the heat generated by the magnetic lines of force cutting in the sealing cover to be carried away in time, preventing the outer magnet 4 and inner magnet 5 from reducing their strength and weakening their magnetism due to excessive temperature. This ensures that the magnets work within a suitable temperature range, thereby improving the working efficiency of the magnetic coupler and extending its service life.

[0056] To further determine the working state of the booster turbine 7 and the centrifugal impeller 8, and to ensure the rationality and optimal effect of the design, we conducted a comparative flow field simulation experiment on the original magnetic coupler and the technical solution of this application during the design phase.

[0057] like Figure 7The diagram shows a comparison of flow field simulation cloud maps at 100 rpm: The longitudinal velocity cloud map shows that without the booster turbine 7 and centrifugal impeller 8, the average velocity of the cooling water in the magnetic coupler at 100 rpm is approximately 0.4 m / s. With the booster turbine 7 and centrifugal impeller 8 added, the flow velocity within the booster turbine 7 at the bottom of the magnetic coupler and the centrifugal impeller 8 at the top is significantly increased, reaching an average velocity of approximately 1.0 m / s. The water flow velocity within the gap is not clearly simulated due to the small gap size, but based on the flow velocity within the booster turbine 7 and centrifugal impeller 8, it can be inferred that the water flow velocity within the gap should be equal to or higher than the water flow velocity within the impeller.

[0058] like Figure 8 As shown, the flow field simulation cloud diagrams at 200 rpm are compared: the longitudinal velocity cloud diagrams show that at 200 rpm, the average velocity of the cooling water in the magnetic coupler without the turbocharger 7 and centrifugal impeller 8 is 0.8 m / s. After adding the turbocharger 7 and centrifugal impeller 8, the average velocity of the cooling water increases to 1.43 m / s, and the maximum flow velocity reaches 2.0 m / s; at the same time, the flow velocity in the gap also increases to between 1.4 and 1.8 m / s.

[0059] like Figure 9 As shown in the trace diagram, analysis of the trace distribution reveals that the flow within the gap between the uncharged turbine 7 and the centrifugal impeller 8 is circumferential with very little axial flow, indicating that cooling water passage is difficult and the allowance is small. After adding the turbocharged turbine 7 and the centrifugal impeller 8, the turbulence effect at the bottom and top is significantly enhanced, and a high-velocity spiraling axial flow is formed within the gap, indicating a substantial increase in cooling water flow rate and a significant enhancement effect.

[0060] In summary, the ANSYS Fluent flow field simulation (CFD) shows that:

[0061] After adding the booster turbine 7 and centrifugal impeller 8, both the average flow velocity within the magnetic coupler and the flow velocity within the gap are significantly improved. At 100 rpm, the average velocity within the gap of the magnetic coupler with booster turbine 7 and centrifugal impeller 8 is 0.6 m / s higher than that without the impeller; at 200 rpm, it is 0.63 m / s to 1.2 m / s higher. The flow pattern within the magnetic coupler is basically circumferential. After adding booster turbine 7 and centrifugal impeller 8, there is some disturbance at the top and bottom, and a strong axial flow is formed within the air gap, ultimately resulting in a strong spiral upward flow.

[0062] Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the appended claims and their equivalents.

[0063] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" 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 utility model based on the specific circumstances.

Claims

1. A forced circulation cooling device for a magnetic coupler, comprising a driver (1), a flange (2), a supporting water jacket (3), an outer magnet (4), an inner magnet (5), and a sealing cover (6), characterized in that: A booster turbine (7) is provided on the bottom end face of the outer magnetic steel body (4). The booster turbine (7) rotates synchronously with the outer magnetic steel body (4). The turbine blades (71) of the booster turbine (7) are streamlined curved surfaces facing the direction of rotation.

2. The forced circulation cooling device for a magnetic coupler according to claim 1, characterized in that, A centrifugal impeller (8) is axially mounted on the flange (2), and centrifugal blades (81) are evenly distributed around the circumference of the centrifugal impeller (8); an axially connected cooling water rising channel is formed between the flange (2) and the centrifugal impeller (8).

3. A forced circulation cooling device for a magnetic coupler according to claim 2, characterized in that, The centrifugal blades (81) divide the centrifugal impeller (8) into multiple centrifugal chambers (82), and each centrifugal chamber (82) has a corresponding cooling water rising channel at its bottom. The centrifugal blades (81) of the centrifugal impeller (8) are streamlined surfaces facing away from the direction of rotation.

4. A forced circulation cooling device for a magnetic coupler according to claim 2, characterized in that, The cooling water rising channel includes: The first flow channel holes (83) on the flange face of the flange (2) are arranged in a ring array; the second flow channel holes (84) on the centrifugal impeller (8) are arranged in a one-to-one correspondence between the first flow channel holes (83) and the second flow channel holes (84).

5. A forced circulation cooling device for a magnetic coupler according to claim 2, characterized in that, The centrifugal impeller (8) is fixedly installed on the flange (2), and the flange (2) is fixedly connected to the outer magnet (4).

6. A forced circulation cooling device for a magnetic coupler according to claim 1, characterized in that, A water seal (9) is installed at the bottom inner side of the turbocharger (7), and the water seal (9) forms a dynamic sealing structure with radial interference fit with the outer surface of the sealing cover (6).

7. A forced circulation cooling device for a magnetic coupler according to claim 1, characterized in that, The turbine blades (71) are evenly distributed around the circumference of the booster turbine (7), and the extension direction of the curved surface of the turbine blades (71) forms an acute angle with the rotation direction.

8. A forced circulation cooling device for a magnetic coupler according to claim 1, characterized in that, The supporting water jacket (3) is provided with a cooling water inlet (31), a cooling water outlet (32) and a cooling water overflow outlet (33); the cooling water inlet (31) is located at the bottom of the supporting water jacket (3), and the cooling water outlet (32) and the overflow outlet (33) are located at the top of the supporting water jacket (3).

9. A forced circulation cooling device for a magnetic coupler according to claim 1, characterized in that, The booster turbine (7) is fixedly installed on the outer magnet (4). An annular narrow gap is formed between the inner flow channel of the booster turbine (7) and the outer surface of the sealing cover (6). The annular narrow gap corresponds to the gap between the outer magnet (4) and the sealing cover (6).

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