Magnetic drive pump with single supporting shaft

Abstract

The invention provides a magnetic drive pump with a single supporting shaft, and belongs to the technical field of pumps. The technical problem that an existing magnetic pump is prone to leakage is solved. The single-supporting-shaft magnetic drive pump comprises a pump shell, a motor shell, a stator assembly, a rotor assembly and an impeller, a first shielding sleeve and a second shielding sleeve are fixedly connected between the pump shell and the motor shell in a sealed mode, the first shielding sleeve is sunken to form a concave cavity opposite to a containing cavity in the radial direction, the concave cavity is communicated with an inlet, and the rotor assembly is located in the concave cavity; the first shielding sleeve is located at the bottom of the concave cavity and protrudes to form a first supporting part coaxial with the concave cavity back to an opening of the concave cavity, a first supporting groove is formed in the first supporting part, an opening of the first supporting groove faces the concave cavity and is communicated with the concave cavity, and a supporting shaft is fixedly connected in the first supporting groove; the end, away from the first supporting groove, of the supporting shaft is embedded into the rotor shaft sleeve and slidably connected with the rotor shaft sleeve. It is guaranteed that the impeller can enter the inlet more smoothly, and the supporting shaft can better support the impeller to rotate.

Description

Technical Field

[0001] The present invention relates to the technical field of pumps, and specifically to a single-support shaft magnetic pump. Background Art

[0002] Magnetic pumps adopt non-contact magnetic coupling drive. The motor drives the outer magnetic rotor, and through the magnetic field, drives the inner magnetic rotor and the pump shaft in the isolation sleeve to rotate, driving the impeller to work. Its key structure lies in the isolation sleeve between the inner and outer magnetic rotors. It completely seals the pump shaft and the inner magnetic rotor, not only preventing leakage along the shaft, but also cooling the internal components. Excellent sealing performance can be achieved without dynamic sealing, so it is widely used in transporting corrosive, flammable, explosive and other dangerous media.

[0003] In the prior art, the installation structure of the pump shaft is as in the structure improvement of the permanent magnet canned pump with the patent number 2011103300199. The first disclosed is a double-sided support fixed shaft structure. The front end of the pump shaft is supported by a tripod fixed at the inlet of the pump front cover. The tripod axially passes through the impeller split hole. The rear end of the pump shaft is inserted into the shaft hole seat at the bottom of the rear cover, and the shaft hole seat is tightly combined and reinforced by the shaft support seat of the metal motor rear frame. It extends through the shaft hole seat to the inner diameter space of the motor rotor main yoke iron, shortening the force arm and enhancing the rigidity. However, this tripod is directly located in the fluid inlet path, forming a mechanical obstacle, destroying the uniformity of the flow field, increasing the fluid resistance, and reducing the suction efficiency. It also discloses the second is a single-sided cantilever composite shaft structure. The support method depends only on the single-sided support of the motor rear frame. The pump shaft is composed of a ceramic shaft sleeve and a metal shaft. The metal shaft passes through the ceramic shaft sleeve, and the head is sealed with an O-ring and locked with a nut on the motor rear frame to form a cantilever compression structure and perform sealing. However, although the single-sided support structure solves the problem of fluid resistance at the inlet, due to the mismatch of the thermal expansion coefficients of the materials, the linear expansion coefficient of the metal shaft is about 18×10⁻ 6 / K, which is quite different from the linear expansion coefficient of 6×10⁻ 6 / K of the ceramic shaft sleeve. When transporting high-temperature media, the metal expansion is far greater than that of the ceramic, which will cause the O-ring to be over-compressed and deformed, resulting in seal failure. And if the pre-tightening force is insufficient when locking with the nut, it will cause leakage at the sealing surface. Over-tightening may extrude and damage the O-ring, which will easily cause leakage, resulting in corrosion of the metal shaft and affecting the normal use of the pump. How to ensure smoother entry at the inlet and enable the support shaft to better support the rotation of the impeller. Summary of the Invention

[0004] Aiming at the deficiencies of the prior art, the purpose of the present invention is to provide a single-support shaft magnetic pump.

[0005] The object of the present invention can be achieved by the following technical solutions: A single-support shaft magnetic pump includes a pump housing and a motor housing fixedly connected. A stator assembly, a rotor assembly, and an impeller fixedly connected to the rotor assembly are arranged in the pump housing and the motor housing. The pump housing has an inlet and an outlet. A first shielding sleeve and a second shielding sleeve are fixedly connected in a sealed manner between the pump housing and the motor housing. A closed accommodation cavity is formed between the first shielding sleeve and the second shielding sleeve. The stator assembly is located in the accommodation cavity. The first shielding sleeve is recessed to form a concave cavity radially opposite to the accommodation cavity. The concave cavity communicates with the inlet. The rotor assembly is located in the concave cavity. The first shielding sleeve protrudes from the bottom of the concave cavity and facing away from the opening of the concave cavity with a first support portion coaxial with the concave cavity. A first support groove is arranged in the first support portion. The opening of the first support groove faces the concave cavity and communicates with the concave cavity. A support shaft is fixedly connected in the first support groove. The rotor assembly includes a rotor shaft sleeve. One end of the support shaft away from the first support groove is embedded in the rotor shaft sleeve and is slidably connected to the rotor shaft sleeve.

[0006] In this solution, one end of the support shaft is fixed by the first support groove coaxial with and in the opposite direction to the concave cavity. The other end of the support shaft cooperates with the rotor shaft sleeve to rotate and drive the impeller to rotate, completely avoiding the mainstream channel area of the inlet, realizing a stable single-support mode. The inlet fluid can directly flow to the center of the impeller without hindrance, evenly and smoothly, greatly reducing the fluid resistance loss, and significantly improving the suction performance and overall efficiency of the pump. The closed accommodation cavity formed by the first shielding sleeve and the second shielding sleeve has completely isolated the stator assembly from the pumped medium. The concave cavity and the first support groove form a structure without leakage points and can stably support the rotation of the support shaft, completely eliminating the most easily failed sealing ring locking seal in the prior art, and completely transferring the sealing responsibility to the static and firm first shielding sleeve and second shielding sleeve, ensuring the long-term reliable operation of the sliding fit between the support shaft and the rotor shaft sleeve, realizing a leak-free operation with high reliability and maintenance-free, especially suitable for the transportation of high-temperature, corrosive, and dangerous media.

[0007] Further, a reinforcing plate is arranged in the accommodation cavity. The reinforcing plate abuts against and is fixedly arranged at the bottom of the second shielding sleeve. The reinforcing plate is provided with fixing holes. The first support groove passes through the fixing holes and abuts against and is fixed to the fixing holes. The reinforcing plate and the second shielding sleeve are integrally formed by embedding, so that the first support groove receives a greater radial fixing force, making the single-sided fixed support shaft more stable.

[0008] Further, a cylindrical fixing portion protrudes from the bottom of the second shielding sleeve facing away from the accommodation cavity. The cylindrical fixing portion is arranged coaxially with the first support groove. The first support groove passes through the cylindrical fixing portion and abuts against and is fixed to the inner hole of the cylindrical fixing portion.

[0009] Furthermore, a frequency converter cover is also provided inside the motor housing. A frequency converter partition is fixedly connected between the frequency converter cover and the second shielding sleeve. There is a support cavity between the second shielding sleeve and the frequency converter partition. The frequency converter partition has partition holes. The cylindrical fixing part passes through the partition holes and abuts and fixes against the partition holes. The cylindrical fixing part, as a rigid extension structure of the second shielding sleeve, provides a second radial support point for the first support groove and the support shaft, significantly shortening the effective cantilever length of the support shaft, reducing flexural deformation, dispersing the impeller load to the second shielding sleeve, suppressing vibration, and enhancing the rotational stability of the rotor assembly. The support cavity between the second shielding sleeve and the frequency converter partition gives axial extension space to the first support groove, increasing the length of the embedded section of the support shaft, and can also isolate the heat transfer between the motor and the frequency converter.

[0010] Furthermore, a number of first reinforcing ribs protrude from the bottom of the second shielding sleeve facing away from the accommodating cavity, and a number of second reinforcing ribs protrude from the frequency converter partition towards the second shielding sleeve. The first reinforcing ribs and the second reinforcing ribs protrude in a radial or grid pattern, greatly enhancing the local bending stiffness.

[0011] Furthermore, a frequency conversion cavity is formed between the frequency converter partition and the frequency converter cover. A frequency conversion device is fixedly arranged in the frequency conversion cavity. The frequency converter cover protrudes with a number of heat dissipation fins in a direction away from the frequency converter partition. The width of the heat dissipation fins is greater than the width of the frequency conversion cavity. This solution enhances the stiffness of the frequency converter cover and its ability to resist deformation, thereby ensuring the sealing performance of the frequency conversion cavity, the stability of internal components, and long-term reliability.

[0012] Furthermore, the rotor assembly further includes a rotor shielding sleeve. The rotor shaft sleeve is fixedly embedded in the rotor shielding sleeve. A thrust piece is fixedly arranged in the concave cavity. The thrust piece is sleeved outside the support shaft with a clearance fit. The upper part of the thrust piece abuts against and rotates in cooperation with the lower part of the rotor shaft sleeve.

[0013] Furthermore, a passage hole is provided at the upper end of the rotor shielding sleeve. The passage hole, the support shaft, and the inlet are relatively arranged.

[0014] Furthermore, the impeller has a through hole that penetrates up and down. The through hole communicates the inlet and the passage hole. A spiral channel is provided on the inner peripheral wall of the rotor shaft sleeve. The spiral channel communicates with the passage hole and the concave cavity.

[0015] Furthermore, the rotor shaft sleeve is made of silicon carbide, and the support shaft is made of ceramic. Silicon carbide and ceramic achieve self-lubricating rotation under oil-free and grease-free conditions. The support shaft not only bears the rotational force but also has corrosion resistance. The support shaft can be in the medium for a long time and can also utilize the medium for cooling and lubrication.

[0016] Compared with the prior art, the present invention has the following technical effects: First, by fixing one side of the support shaft in the first support groove protruding from the bottom back side of the first shielding sleeve cavity, the inlet fluid can flow directly to the center of the impeller without any obstruction, evenly and smoothly, without having to bypass any support structure. This minimizes fluid resistance loss and significantly improves the pump's suction performance and overall hydraulic efficiency. Second, one end of the support shaft is deeply embedded and firmly fixed in the first support groove on the back side of the cavity bottom. Rigidity is enhanced by the reinforcing plate and cylindrical fixing portion. The cylindrical fixing portion extending from the second shielding sleeve passes through the baffle hole of the inverter partition, providing a second radial support point for the support shaft, increasing the constraint of the support shaft near the impeller end, significantly shortening the effective cantilever length of the support shaft, greatly reducing the deflection deformation caused by centrifugal force of the rotor assembly and impeller, and distributing the impeller load. Part of the load is transferred through the cylindrical fixing portion to the more rigid second shielding sleeve and inverter partition structure, enhancing the rigidity of the entire rotor system, effectively suppressing vibration, and significantly improving the rotational stability of the rotor assembly. 3. The inlet fluid passes through the impeller through-hole and the passage hole, enters the spiral channel of the rotor sleeve, and finally flows into the fitting clearance and the concave cavity between the support shaft and the rotor sleeve, continuously lubricating the sliding friction pair of the support shaft and the rotor sleeve, reducing friction and wear. The flowing fluid also takes away the heat generated by friction, effectively cooling the support shaft and bearing parts. The lubrication and cooling by the pumping medium itself ensures the reliability and life of the support shaft in long-term operation in high temperature and corrosive environments. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 It is a cross-sectional view of the present invention.

[0018] Figure 2 It is a cross-sectional view of the stator assembly, rotor assembly, impeller, first shielding sleeve, second shielding sleeve and inverter partition of the present invention.

[0019] Figure 3 It is a cross-sectional view of the present invention with the pump housing and the motor housing removed.

[0020] Figure 4 It is a cross-sectional view of the stator assembly, the first shielding sleeve and the second shielding sleeve of the present invention.

[0021] Figure 5 It is a stereoscopic view of the stator assembly, the first shielding sleeve and the second shielding sleeve of the present invention.

[0022] Figure 6 It is a three-dimensional diagram of the inverter partition of the second shielding sleeve of the present invention.

[0023] Figure number markings: 1, pump housing; 101, inlet; 102, outlet; 2, motor housing; 3, stator assembly; 4, rotor assembly; 401, rotor shaft sleeve; 4011, spiral channel; 402, rotor shielding sleeve; 403, aisle hole; 5, impeller; 501, through hole; 6, first shielding sleeve; 601, concave cavity; 602, first support portion; 603, first support groove; 7, second shielding sleeve; 701, cylindrical fixing portion; 702, first reinforcing rib; 8, support shaft; 9, reinforcing plate; 901, fixing hole; 10, frequency converter cover; 1002, frequency conversion cavity; 1001, heat sink; 11, frequency converter partition; 1101, partition hole; 1102, second reinforcing rib; 12, support cavity; 13, frequency conversion device; 14, thrust piece; 15, fastener. Detailed implementation mode

[0024] The following are specific embodiments of the present invention in combination with the accompanying drawings to further describe the technical solutions of the present invention, but the present invention is not limited to these embodiments.

[0025] It should be noted that the descriptions of the present invention in terms of directions such as "upper", "lower", "left", "right", "top", "bottom", etc. are all defined based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device must be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation of the present invention.

[0026] According to Figures 1 to 6As shown in the figure, a single-support shaft magnetic pump includes a pump casing 1 and a motor casing 2 fixedly connected by a fastener 15. A stator assembly 3, a rotor assembly 4, and an impeller 5 fixedly connected to the rotor assembly 4 are arranged inside the pump casing 1 and the motor casing 2. The pump casing 1 has an inlet 101 and an outlet 102, and the impeller 5 is arranged opposite to the inlet 101 and the outlet 102 of the pump casing 1. The impeller 5 and the rotor assembly 4 can be integrally formed or fixedly connected by a buckle. The stator assembly 3 is integrally formed by several permanent magnets. A first shielding sleeve 6 and a second shielding sleeve 7 are hermetically and fixedly connected between the pump casing 1 and the motor casing 2. A closed accommodating cavity is formed between the first shielding sleeve 6 and the second shielding sleeve 7, and the closed accommodating cavity is fully enclosed. The stator assembly 3 is located inside the accommodating cavity. A concave cavity 601 radially opposite to the accommodating cavity is formed by the depression of the first shielding sleeve 6. The concave cavity 601 is communicated with the inlet 101, and the rotor assembly 4 is located inside the concave cavity 601. The rotor assembly 4 rotates relative to the stator assembly 3. A first support portion 602 coaxial with the concave cavity 601 protrudes from the bottom of the first shielding sleeve 6 located in the concave cavity 601 and facing away from the opening of the concave cavity 601. A first support groove 603 is arranged inside the first support portion 602. The opening of the first support groove 603 faces the concave cavity 601 and is communicated with the concave cavity 601. A support shaft 8 is fixedly connected inside the first support groove 603. The rotor assembly 4 includes a rotor shaft sleeve 401. One end of the support shaft 8 away from the first support groove 603 is embedded inside the rotor shaft sleeve 401 and is slidably connected with the rotor shaft sleeve 401. A single support structure is formed by arranging the first support groove 603 coaxial with the concave cavity 601 and in the opposite direction to fix one end of the support shaft 8. The other end of the support shaft 8 cooperates with the rotor shaft sleeve 401 to rotate and drive the impeller 5 to rotate, completely avoiding the mainstream channel area of the inlet 101, realizing a stable single support mode. The fluid at the inlet 101 can flow directly to the center of the impeller 5 without obstruction, evenly and smoothly, greatly reducing the fluid resistance loss, and significantly improving the suction performance and overall efficiency of the pump. The closed accommodating cavity formed by the first shielding sleeve 6 and the second shielding sleeve 7 has completely isolated the stator assembly 3 from the pumped medium. The concave cavity 601 and the first support groove 603 form a structure without leakage points and can stably support the rotation of the support shaft 8. The sealing ring that is most likely to fail in the prior art is completely eliminated, and the sealing responsibility is completely transferred to the static and firm first shielding sleeve 6 and second shielding sleeve 7, ensuring the long-term reliable operation of the sliding fit between the support shaft 8 and the rotor shaft sleeve 401, realizing a leak-free operation with high reliability and maintenance-free, especially suitable for the transportation of high-temperature, corrosive, and dangerous media. A reinforcing plate 9 is arranged inside the accommodating cavity. The reinforcing plate 9 abuts against the bottom of the second shielding sleeve 7 and is fixedly arranged. The reinforcing plate 9 is provided with a fixing hole 901. The first support groove 603 passes through the fixing hole 901 and abuts against the fixing hole 901 for fixation. The reinforcing plate 9 and the second shielding sleeve 7 are integrally formed by embedding, so that the first support groove 603 receives a greater radial fixing force, making the single-sided fixed support shaft 8 more stable.The bottom of the second shielding sleeve 7 protrudes from the accommodating cavity with a cylindrical fixing part 701. The cylindrical fixing part 701 is coaxially arranged with the first support groove 603. The first support groove 603 passes through the cylindrical fixing part 701 and abuts and fixes against the inner hole of the cylindrical fixing part 701. The stator assembly 3 is integrally formed; the reinforcing plate 9 and the second shielding sleeve 7 are integrally formed; the stator assembly 3, the reinforcing plate 9 and the second shielding sleeve 7 can be integrally formed together; the first shielding sleeve 6, the stator assembly 3, the reinforcing plate 9 and the second shielding sleeve 7 can be integrally formed together.

[0027] A frequency converter cover 10 is further arranged in the motor housing 2. A frequency converter partition plate 11 is fixedly connected between the frequency converter cover 10 and the second shielding sleeve 7. There is a support cavity 12 between the second shielding sleeve 7 and the frequency converter partition plate 11. The frequency converter partition plate 11 has a partition hole 1101. The cylindrical fixing part 701 passes through the partition hole 1101 and abuts and fixes against the partition hole 1101. The cylindrical fixing part 701 serves as a rigid extension structure of the second shielding sleeve 7, provides a second radial support point for the first support groove 603 and the support shaft 8, significantly shortens the effective cantilever length of the support shaft 8, reduces the flexural deformation, disperses the load of the impeller 5 to the second shielding sleeve 7, suppresses the vibration, and improves the rotational stability of the rotor assembly 4. The support cavity 12 between the second shielding sleeve 7 and the frequency converter partition plate 11 gives axial extension space to the first support groove 603, makes the embedded section of the support shaft 8 longer, and can also isolate the heat transfer between the motor and the frequency converter. The bottom of the second shielding sleeve 7 protrudes from the accommodating cavity with a plurality of first reinforcing ribs 702. The frequency converter partition plate 11 protrudes towards the second shielding sleeve 7 with a plurality of second reinforcing ribs 1102. The first reinforcing ribs 702 and the second reinforcing ribs 1102 protrude in a radial or grid shape, greatly improving the local bending stiffness.

[0028] A frequency conversion cavity 1002 is formed between the frequency converter partition plate 11 and the frequency converter cover 10. A frequency conversion device 13 is fixedly arranged in the frequency conversion cavity 1002. The frequency converter cover 10 protrudes towards the direction away from the frequency converter partition plate 11 with a plurality of heat dissipation fins 1001. The width of the heat dissipation fins 1001 is greater than the width of the frequency conversion cavity 1002. This solution improves the stiffness of the frequency converter cover 10 and the ability to resist deformation, thereby ensuring the sealing performance of the frequency conversion cavity 1002, the stability of the internal components, and the long-term reliability.

[0029] The rotor assembly 4 also includes a rotor shield 402. The rotor assembly 4 is integrally formed, with a rotor sleeve 401 fixedly embedded within the sleeve. A thrust member 14 is fixedly mounted within the cavity 601. The thrust member 14 is loosely fitted around the support shaft 8, with the upper portion of the thrust member 14 abutting and rotatably engaging with the lower portion of the rotor sleeve 401. A passageway hole 403 is provided at the upper end of the rotor shield 402. The passageway hole 403, the support shaft 8, and the inlet 101 are all positioned relative to each other. The impeller 5 has a through-hole 501 extending vertically therethrough, connecting the inlet 101 with the passageway hole 403. A spiral channel 4011 is provided on the inner circumferential wall of the rotor sleeve 401, connecting the passageway hole 403 and the cavity 601. The rotor sleeve 401 is made of silicon carbide, and the support shaft 8 is made of ceramic. Silicon carbide and ceramics realize self-lubricating rotation under oil-free and grease-free conditions. The support shaft 8 can bear the rotational force and is corrosion-resistant. The support shaft 8 can be in the medium for a long time and can also use the medium for cooling and lubrication.

[0030] One side of the support shaft 8 is fixed in the first support groove 603 protruding from the bottom back side of the concave cavity 601 of the first shielding sleeve 6, so that the fluid at the inlet 101 does not need to bypass any supporting structure and can flow directly to the center of the impeller 5 without obstruction, evenly and smoothly. This minimizes the fluid resistance loss and significantly improves the suction performance and overall hydraulic efficiency of the pump. One end of the support shaft 8 is deeply embedded in and firmly fixed in the first support groove 603 on the back side of the bottom of the cavity 601, and the rigidity is enhanced by the reinforcing plate 9 and the cylindrical fixing part 701. The cylindrical fixing part 701 extending from the second shielding sleeve 7 passes through the partition hole 1101 of the inverter partition 11, providing a second radial support point for the support shaft 8, increasing the constraint of the support shaft 8 close to the end of the impeller 5, which can significantly shorten the effective cantilever length of the support shaft 8, greatly reducing the flexural deformation caused by the centrifugal force of the rotor assembly 4 and the impeller 5, and dispersing the load on the impeller 5. Part of the load is transmitted to the more solid second shielding sleeve 7 and the inverter partition 11 structure through the cylindrical fixing part 701, thereby enhancing the rigidity of the entire rotor system and effectively suppressing vibration, thereby greatly improving the rotation stability of the rotor assembly 4. The fluid at the inlet 101 passes through the through hole 501 of the impeller 5 and the passage hole 403, enters the spiral channel 4011 of the rotor sleeve 401, and finally flows into the fitting clearance between the support shaft 8 and the rotor sleeve 401 and the concave cavity 601, continuously lubricating the sliding friction pair of the support shaft 8 and the rotor sleeve 401, reducing friction and wear. The flowing fluid also takes away the heat generated by friction, effectively cooling the support shaft 8 and the bearing parts. The lubrication and cooling performed by the pumping medium itself ensure the reliability and life of the support shaft 8 in long-term operation in a high-temperature and corrosive environment.

[0031] The above embodiments are only preferred embodiments of the present invention, and do not limit the protection scope of the present invention accordingly. Therefore, all equivalent changes made according to the structure, shape, and principle of the present invention shall be covered by the protection scope defined by the claims of the present invention.

Claims

1. A single-supported shaft magnetic pump, comprising a pump housing (1) and a motor housing (2) fixedly connected. A stator assembly (3), a rotor assembly (4), and an impeller (5) fixedly connected to the rotor assembly (4) are arranged in the pump housing (1) and the motor housing (2). The pump housing (1) has an inlet (101) and an outlet (102), and is characterized in that: A first shielding sleeve (6) and a second shielding sleeve (7) are hermetically and fixedly connected between the pump housing (1) and the motor housing (2). A closed accommodating cavity is formed between the first shielding sleeve (6) and the second shielding sleeve (7). The stator assembly (3) is located in the accommodating cavity. The first shielding sleeve (6) is recessed to form a concave cavity (601) radially opposite to the accommodating cavity. The concave cavity (601) is communicated with the inlet (101). The rotor assembly (4) is located in the concave cavity (601). The first shielding sleeve (6) protrudes from the bottom of the concave cavity (601) and facing away from the opening of the concave cavity (601) to form a first support portion (602) coaxial with the concave cavity (601). A first support groove (603) is provided in the first support portion (602). The opening of the first support groove (603) faces the concave cavity (601) and is communicated with the concave cavity (601). A support shaft (8) is fixedly connected in the first support groove (603). The rotor assembly (4) includes a rotor shaft sleeve (401). One end of the support shaft (8) away from the first support groove (603) is embedded in the rotor shaft sleeve (401) and is slidably connected with the rotor shaft sleeve (401).

2. The single-support shaft magnetic pump according to claim 1, characterized in that: A reinforcing plate (9) is provided in the accommodating cavity. The reinforcing plate (9) abuts against and is fixedly arranged at the bottom of the second shielding sleeve (7). The reinforcing plate (9) is provided with a fixing hole (901). The first support groove (603) passes through the fixing hole (901) and abuts against and is fixed to the fixing hole (901).

3. The single-support shaft magnetic pump according to claim 2, wherein: A cylindrical fixing portion (701) protrudes from the bottom of the second shielding sleeve (7) facing away from the accommodating cavity. The cylindrical fixing portion (701) is coaxially arranged with the first support groove (603). The first support groove (603) passes through the cylindrical fixing portion (701) and abuts against and is fixed to the inner hole of the cylindrical fixing portion (701).

4. The single-support shaft magnetic pump according to claim 3, characterized in that: A frequency converter cover (10) is further provided in the motor housing (2). A frequency converter partition plate (11) is fixedly connected between the frequency converter cover (10) and the second shielding sleeve (7). A support cavity (12) is formed between the second shielding sleeve (7) and the frequency converter partition plate (11). A partition hole (1101) is formed in the frequency converter partition plate (11). The cylindrical fixing portion (701) passes through the partition hole (1101) and abuts against and is fixed to the partition hole (1101).

5. The single-support shaft magnetic pump according to claim 4, characterized in that: A plurality of first reinforcing rib strips (702) protrude from the bottom of the second shielding sleeve (7) facing away from the accommodating cavity. A plurality of second reinforcing rib strips (1102) protrude from the frequency converter partition plate (11) towards the second shielding sleeve (7).

6. The single-support shaft magnetic pump according to claim 4, wherein: A frequency conversion cavity (1002) is formed between the frequency converter partition plate (11) and the frequency converter cover (10). A frequency conversion device (13) is fixedly arranged in the frequency conversion cavity (1002). A plurality of heat dissipation fins (1001) protrude from the frequency converter cover (10) in a direction away from the frequency converter partition plate (11). The width of the heat dissipation fins (1001) is greater than the width of the frequency conversion cavity (1002).

7. A single-supported shaft magnetic pump according to any one of claims 1 to 6, characterized in that: The rotor assembly (4) further includes a rotor shield sleeve (402). The rotor shaft sleeve (401) is fixedly embedded in the rotor shield sleeve (402). A thrust member (14) is fixedly arranged in the concave cavity (601). The thrust member (14) is sleeved outside the support shaft (8) with a clearance fit. The upper part of the thrust member (14) abuts against and rotates in cooperation with the lower part of the rotor shaft sleeve (401).

8. A single-support shaft magnetic pump according to claim 7, characterized in that: An aisle hole (403) is provided at the upper end of the rotor shield sleeve (402). The aisle hole (403), the support shaft (8), and the inlet (101) are relatively arranged.

9. The single-support shaft magnetic pump according to claim 8, wherein: The impeller (5) has a through hole (501) that penetrates up and down. The through hole (501) communicates with the inlet (101) and the aisle hole (403). A spiral channel (4011) is provided on the inner peripheral wall of the rotor shaft sleeve (401). The spiral channel (4011) communicates with the aisle hole (403) and the concave cavity (601).

10. The single-support shaft magnetic pump according to claim 1, characterized in that: The rotor shaft sleeve (401) is made of silicon carbide, and the support shaft (8) is made of ceramics.

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