A single support shaft magnetic pump

Abstract

The present invention provides a single-shaft magnetic pump, which belongs to the field of pump technology. It solves technical problems such as the easy leakage of existing magnetic pumps. The single-shaft magnetic pump includes a pump housing, a motor housing, a stator assembly, a rotor assembly, and an impeller. A first shielding sleeve and a second shielding sleeve are sealed and fixedly connected between the pump housing and the motor housing. The first shielding sleeve is recessed to form a cavity radially opposite to the accommodating cavity, and the cavity is connected to the inlet. The rotor assembly is located in the cavity. The first shielding sleeve is located at the bottom of the cavity and faces away from the cavity opening. A first support portion coaxial with the cavity is protruded. A first support groove is provided in the first support portion. The opening of the first support groove faces the cavity and is connected to the cavity. A support shaft is fixedly connected in the first support groove. The rotor assembly includes a rotor sleeve. The end of the support shaft away from the first support groove is embedded in the rotor sleeve and is slidably connected to the rotor sleeve. The present invention ensures smoother entry at the inlet and enables the support shaft to better support the rotation of the impeller.

Description

Technical Field

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

[0002] Magnetic drive pumps utilize contactless magnetic coupling. A motor drives an outer magnetic rotor, which, through the magnetic field, rotates the inner magnetic rotor and pump shaft within the isolation sleeve, driving the impeller. The key structure lies in the isolation sleeve between the inner and outer magnetic rotors. This completely seals the pump shaft and inner magnetic rotor, eliminating leakage along the shaft while also cooling internal components. This achieves excellent sealing without the need for dynamic sealing, making it widely used in conveying corrosive, flammable, and explosive hazardous media.

[0003] Existing pump shaft mounting structures, such as those described in Patent No. 2011103300199, offer improvements to the permanent magnet canned pump structure. The patent discloses a first dual-sided fixed-shaft structure, in which the front end of the pump shaft is supported by a tripod fixed to the pump front cover entrance, extending axially through the impeller aperture. The rear end of the pump shaft is inserted into a shaft hole seat at the bottom of the rear cover, where it is tightly coupled and reinforced by the shaft support seat on the metal motor rear frame. This hole seat extends into the inner diameter of the motor rotor main yoke, shortening the lever arm and enhancing rigidity. However, the tripod is located directly in the fluid inlet path, creating a mechanical obstruction that disrupts flow field uniformity, increases fluid resistance, and reduces suction efficiency. The patent also discloses a second single-sided cantilever composite shaft structure, supported only by the motor rear frame. The pump shaft is constructed from a ceramic sleeve and a metal shaft. The metal shaft passes through the ceramic sleeve, its head sealed with an O-ring, and a nut locks onto the motor rear frame, forming a cantilever compression structure and providing a seal. However, although the unilateral support structure solves the problem of fluid resistance at the inlet, due to the mismatch of material thermal expansion coefficients, the linear expansion coefficient of the metal shaft is about 18×10⁻ 6 / K and the linear expansion coefficient of the ceramic bushing are 6×10⁻ 6 The large difference in K / K between the two materials, coupled with the fact that metal expands much more than ceramic when conveying high-temperature media, can lead to excessive compression and deformation of the O-ring, resulting in seal failure. Furthermore, insufficient preload during nut tightening can cause leakage on the sealing surface, while overtightening can squeeze out and damage the O-ring, easily causing leakage and corrosion of the metal shaft, impacting the pump's proper operation. How can we ensure smoother inlet flow and better support for the impeller's rotation through the support shaft? Summary of the Invention

[0004] In view of the shortcomings of the prior art, the present invention aims to provide a single-support shaft magnetic pump.

[0005] The objectives of the present invention can be achieved through the following technical solutions: A single-support shaft magnetic pump, comprising a pump casing and a motor casing fixedly connected, wherein a stator assembly, a rotor assembly and an impeller fixedly connected to the rotor assembly are arranged in the pump casing and the motor casing, the pump casing having an inlet and an outlet, a first shielding sleeve and a second shielding sleeve sealed and fixedly connected between the pump casing and the motor casing, a closed accommodating chamber formed between the first shielding sleeve and the second shielding sleeve, the stator assembly being located in the accommodating chamber, the first shielding sleeve being recessed to form a concave cavity radially opposite to the accommodating chamber, the concave cavity being connected to the inlet, the rotor assembly being located in the concave cavity, the first shielding sleeve having a first support portion protruding from the bottom of the concave cavity and facing away from the opening of the concave cavity, the first support portion being provided with a first support groove, the opening of the first support groove facing the concave cavity and being connected to the concave cavity, a support shaft being fixedly connected in the first support groove, the rotor assembly comprising a rotor sleeve, the end of the support shaft away from the first support groove being embedded in the rotor sleeve and slidably connected to the rotor sleeve.

[0006] This solution fixes one end of the support shaft through a first support groove that is coaxial with the concave cavity and in the opposite direction. The other end of the support shaft rotates in conjunction with the rotor sleeve to drive the impeller, completely avoiding the main flow channel area of ​​the inlet and achieving a stable single support mode. The inlet fluid can flow directly to the center of the impeller without obstruction, evenly and smoothly, greatly reducing 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 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 with no leakage points and can stabilize the rotation of the support shaft, completely eliminating the sealing ring locking seal that is most prone to failure in the existing technology, and completely transferring the sealing responsibility to the static and sturdy first shielding sleeve and the second shielding sleeve, ensuring the long-term reliable operation of the sliding fit between the support shaft and the rotor sleeve, and achieving high reliability, maintenance-free and leak-free operation. It is particularly suitable for the transportation of high-temperature, corrosive and hazardous media.

[0007] Furthermore, a reinforcement plate is provided within the accommodating cavity, abutting and securing the bottom of the second shielding sleeve. The reinforcement plate is provided with a fixing hole, through which the first support groove passes and abuts and secures. The reinforcement plate and the second shielding sleeve are integrally embedded, providing a greater radial securing force on the first support groove and further stabilizing the unilaterally fixed support shaft.

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

[0009] Furthermore, a frequency converter cover is provided within the motor housing. A frequency converter partition is fixedly connected between the frequency converter cover and the second shielding sleeve. A support cavity is provided between the second shielding sleeve and the frequency converter partition. The frequency converter partition has a barrier hole. The cylindrical fixing portion is passed through the barrier hole and fixed against the barrier hole. The cylindrical fixing portion serves as a rigid extension structure of the second shielding sleeve, providing a second radial support point for the first support slot and the support shaft, significantly shortening the effective cantilever length of the support shaft, reducing flexural deformation, distributing the impeller load to the second shielding sleeve, suppressing vibration, and improving the rotational stability of the rotor assembly. The support cavity between the second shielding sleeve and the frequency converter partition provides space for the axial extension of the first support slot, increasing the embedded section of the support shaft and isolating the heat transfer between the motor and the frequency converter.

[0010] Furthermore, the bottom of the second shielding sleeve is provided with a plurality of reinforcing ribs 1, facing away from the accommodating cavity, and the inverter partition is provided with a plurality of reinforcing ribs 2, facing the second shielding sleeve. The reinforcing ribs 1 and 2 are radially or grid-shaped, significantly increasing the local bending stiffness.

[0011] Furthermore, a frequency conversion cavity is formed between the inverter partition and the inverter cover, within which a frequency conversion device is fixed. The inverter cover has a plurality of heat sinks projecting away from the inverter partition, with the width of the heat sinks exceeding that of the frequency conversion cavity. This solution improves the rigidity and deformation resistance of the inverter cover, thereby ensuring the sealing of the frequency conversion cavity, the stability of the internal components, and the long-term reliability.

[0012] Furthermore, the rotor assembly also 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, and the upper part of the thrust piece abuts against and rotates 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, and the passage hole, the support shaft and the inlet are arranged relative to each other.

[0014] Furthermore, the impeller has a through hole running through from top to bottom, the through hole is connected to the inlet and the passage hole, a spiral channel is provided on the inner peripheral wall of the rotor sleeve, and the spiral channel is connected to the passage hole and the concave cavity.

[0015] Furthermore, the rotor sleeve is made of silicon carbide, and the support shaft is made of ceramic. Silicon carbide and ceramic achieve self-lubricating rotation without oil or grease. The support shaft not only bears the rotational force but also has corrosion resistance. The support shaft can be immersed in a medium for a long time and can also be cooled and lubricated by the medium.

[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 marking: 1. Pump casing; 101. Inlet; 102. Outlet; 2. Motor casing; 3. Stator assembly; 4. Rotor assembly; 401. Rotor 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 part; 603. First support groove; 7. Second shielding sleeve; 701. Cylinder fixing part; 702. Reinforcement rib one; 8. Support shaft; 9. Reinforcement plate; 901. Fixing hole; 10. Inverter cover; 1002. Inverter cavity; 1001. Heat sink; 11. Inverter partition; 1101. Partition hole; 1102. Reinforcement rib two; 12. Support cavity; 13. Inverter; 14. Thrust member; 15. Fastener. DETAILED DESCRIPTION

[0024] The following are specific embodiments of the present invention and 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 regarding directions such as "up", "down", "left", "right", "top" and "bottom" are all defined based on the relationships between the orientations or positions shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device must be constructed and operated in a specific orientation. Therefore, they cannot be understood as limitations on the present invention.

[0026] according to Figures 1 to 6As shown, a single-shaft magnetic pump includes a pump housing 1 and a motor housing 2 fixedly connected by fasteners 15. 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 the impeller 5 is arranged relative to the inlet 101 and the outlet 102 of the pump housing 1. The impeller 5 and the rotor assembly 4 can be integrally formed or fixedly connected by snap fasteners. The stator assembly 3 is integrally formed from a plurality of permanent magnets. A first shielding sleeve 6 and a second shielding sleeve 7 are sealed and fixedly connected between the pump housing 1 and the motor housing 2. A closed accommodating chamber is formed between the first shielding sleeve 6 and the second shielding sleeve 7. The closed accommodating chamber is fully enclosed, and the stator assembly 3 is located in the accommodating chamber. The first shielding sleeve 6 is recessed to form a concave cavity 601 radially opposite to the accommodating chamber. The concave cavity 601 is connected to the inlet 101, and the rotor assembly 4 is located in the concave cavity 601. The rotor assembly 4 rotates relative to the stator assembly 3. The first shielding sleeve 6 has a first support portion 602 protruding from the bottom of the cavity 601, facing away from the opening of the cavity 601, coaxial with the cavity 601. A first support groove 603 is provided within the first support portion 602, opening toward and communicating with the cavity 601. A support shaft 8 is fixedly connected within the first support groove 603. The rotor assembly 4 includes a rotor sleeve 401, with the end of the support shaft 8, distal from the first support groove 603, embedded within the rotor sleeve 401 and slidably connected thereto. The first support groove 603, coaxial with and opposite to the cavity 601, secures one end of the support shaft 8, forming a single support structure. The other end of the support shaft 8 rotates in conjunction with the rotor sleeve 401, driving the impeller 5. This completely avoids the main flow channel area of ​​the inlet 101, achieving a stable single support mode. Fluid at the inlet 101 can flow directly and smoothly to the center of the impeller 5 without obstruction, evenly, and smoothly, significantly reducing fluid resistance losses and significantly improving the pump's suction performance and overall efficiency. The enclosed housing formed by the first and second shielding sleeves 6 and 7 completely isolates the stator assembly 3 from the pumped medium. The recessed cavity 601 and first support groove 603 form a leak-free structure while also stabilizing the rotation of the support shaft 8. This eliminates the sealing ring lock seal, which is most prone to failure in the prior art, and shifts the sealing responsibility entirely to the static and robust first and second shielding sleeves 6 and 7. This ensures long-term reliable sliding fit between the support shaft 8 and the rotor sleeve 401, achieving high reliability, maintenance-free, and leak-free operation, making it particularly suitable for conveying high-temperature, corrosive, and hazardous media. A reinforcement plate 9 is positioned within the housing, abutting and securing the bottom of the second shielding sleeve 7. The reinforcement plate 9 is provided with a fixing hole 901, through which the first support groove 603 passes and abuts against it. The reinforcement plate 9 is integrally formed with the second shielding sleeve 7, providing a greater radial securing force on the first support groove 603 and further stabilizing the single-sided support shaft 8.A cylindrical fixing portion 701 protrudes from the bottom of the second shielding sleeve 7, facing away from the accommodating cavity. This cylindrical fixing portion 701 is coaxial with the first supporting groove 603. The first supporting groove 603 passes through the cylindrical fixing portion 701 and abuts against the inner hole of the cylindrical fixing portion 701. The stator assembly 3 is integrally formed; the reinforcement plate 9 and the second shielding sleeve 7 are integrally formed; the stator assembly 3, reinforcement plate 9, and second shielding sleeve 7 can also be integrally formed together; the first shielding sleeve 6, stator assembly 3, reinforcement plate 9, and second shielding sleeve 7 can also be integrally formed together.

[0027] The motor housing 2 also houses an inverter cover 10. An inverter spacer 11 is fixedly connected between the inverter cover 10 and the second shielding sleeve 7. A support cavity 12 is defined between the second shielding sleeve 7 and the inverter spacer 11. The inverter spacer 11 includes a stopper hole 1101, and a cylindrical fixing portion 701 is inserted into and abuts against this hole. The cylindrical fixing portion 701 serves as a rigid extension of the second shielding sleeve 7, providing a second radial support point for the first support slot 603 and the support shaft 8. This significantly shortens the effective cantilever length of the support shaft 8, reduces flexural deformation, distributes the load of the impeller 5 to the second shielding sleeve 7, suppresses vibration, and improves the rotational stability of the rotor assembly 4. The support cavity 12 between the second shielding sleeve 7 and the inverter spacer 11 provides space for the first support slot 603 to extend axially, increasing the embedded length of the support shaft 8 and isolating heat transfer between the motor and the inverter. Several reinforcing ribs 702 protrude from the bottom of the second shielding sleeve 7, facing away from the accommodating cavity. Several reinforcing ribs 1102 protrude from the inverter partition 11 toward the second shielding sleeve 7. The reinforcing ribs 702 and 1102 protrude radially or in a grid pattern, significantly improving the local bending stiffness.

[0028] A frequency conversion cavity 1002 is formed between the inverter partition 11 and the inverter cover 10. A frequency conversion device 13 is fixedly mounted within the frequency conversion cavity 1002. The inverter cover 10 has several heat sinks 1001 projecting away from the inverter partition 11. The width of the heat sinks 1001 is greater than the width of the frequency conversion cavity 1002. This solution improves the rigidity and deformation resistance of the inverter cover 10, thereby ensuring the sealing 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 are not intended to limit the scope of protection of the present invention. Therefore, any equivalent changes made based on the structure, shape, and principle of the present invention should be included in the scope of protection defined by the claims of the present invention.

Claims

1. A single-shaft magnetic pump, comprising a pump housing (1) and a motor housing (2) fixedly connected, wherein 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), wherein 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 sealed 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) is located at the bottom of the concave cavity (601) and faces away from the opening of the concave cavity (601) to protrude with the same diameter as the concave cavity (601) A first support portion (602) of the axis, wherein a first support groove (603) is provided in the first support portion (602), an opening of the first support groove (603) faces the concave cavity (601) and is in communication with the concave cavity (601), a support shaft (8) is fixedly connected in the first support groove (603), the rotor assembly (4) comprises a rotor sleeve (401), an end of the support shaft (8) away from the first support groove (603) is embedded in the rotor sleeve (401) and is slidably connected to the rotor sleeve (401); the rotor sleeve (401) is made of silicon carbide, and the support shaft (8) is made of ceramics; A cylindrical fixing portion (701) is protruded 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 supporting groove (603). The first supporting groove (603) passes through the cylindrical fixing portion (701) and abuts against the inner hole of the cylindrical fixing portion (701). A frequency converter cover (10) is further provided in the motor housing (2); a frequency converter partition (11) is fixedly connected between the frequency converter cover (10) and the second shielding sleeve (7); a supporting cavity (12) is provided between the second shielding sleeve (7) and the frequency converter partition (11); a partition hole (1101) is provided in the frequency converter partition (11); and the cylindrical fixing portion (701) is passed through the partition hole (1101) and abutted against the partition hole (1101).

2. A 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) is abutted against and fixed to the bottom of the second shielding sleeve (7), the reinforcing plate (9) is provided with a fixing hole (901), and the first supporting groove (603) passes through the fixing hole (901) and is abutted against and fixed to the fixing hole (901).

3. A single-support shaft magnetic pump according to claim 2, characterized in that: The bottom of the second shielding sleeve (7) is protruded with a plurality of reinforcing ribs (702) facing away from the accommodating cavity, and the inverter partition (11) is protruded with a plurality of reinforcing ribs (1102) facing the second shielding sleeve (7).

4. A single-support shaft magnetic pump according to claim 2, characterized in that: A frequency conversion cavity (1002) is formed between the frequency converter partition (11) and the frequency converter cover (10), a frequency conversion device (13) is fixedly arranged in the frequency conversion cavity (1002), and the frequency converter cover (10) has a plurality of heat sinks (1001) protruding in a direction away from the frequency converter partition (11), and the width of the heat sinks (1001) is greater than the width of the frequency conversion cavity (1002).

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

6. A single-support shaft magnetic pump according to claim 5, characterized in that: The upper end of the rotor shielding sleeve (402) is provided with a passage hole (403), and the passage hole (403), the support shaft (8) and the inlet (101) are all arranged relative to each other.

7. A single-support shaft magnetic pump according to claim 6, characterized in that: The impeller (5) has a through hole (501) that passes through from top to bottom, the through hole (501) is connected to the inlet (101) and the passage hole (403), and a spiral channel (4011) is provided on the inner peripheral wall of the rotor sleeve (401), and the spiral channel (4011) is connected to the passage hole (403) and the concave cavity (601).

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