A rigid double-support magnetic pump

Abstract

This invention provides a rigid double-support magnetic pump, belonging to the field of pump technology. It solves the technical problems of existing magnetic pumps, such as poor rotor axial stability, low operational reliability, and the risk of leakage due to wear and tear of the shielding sleeve caused by the easy wear of the axial thrust bearing system. This rigid double-support magnetic pump includes a fixedly connected motor housing and a pump housing. The motor housing houses a rotor assembly and a stator assembly, and the pump housing houses an impeller. The rotor assembly is enclosed by a rotor shielding sleeve, and the stator assembly is enclosed by a stator shielding sleeve. The stator shielding sleeve has a fixing groove, in which a first rotating component is fixed. A support partition has a fixing hole, in which a second rotating component is fixed. A support shaft is rotatably connected between the first and second rotating components. The rotor shielding sleeve is fixed to the outer circumference of the support shaft, and the support shaft is fixedly connected to the impeller. This invention has the advantages of achieving axial rigidity constraint of the rotor, significantly reducing wear, and ensuring long-term safe and stable operation.

Description

Technical Field

[0001] This utility model belongs to the field of pump technology, specifically referring to a rigid double-support magnetic pump. Background Technology

[0002] In industrial fields such as chemical and pharmaceutical industries that involve the transportation of highly hazardous media, the shaft seal-free shielded magnetic pump has become a key piece of equipment for transporting highly toxic, highly corrosive, flammable and explosive liquids because it completely eliminates the risk of shaft seal leakage.

[0003] However, the axial stability of the rotor in this type of pump has always been a core challenge limiting its long-term operational reliability. During operation, the axial force generated by the impeller causes axial movement of the rotor assembly. This movement not only causes vibration, noise, and efficiency reduction, but more seriously, it can lead to friction and collision between the rotor and stationary parts such as the pump cover or shielding sleeve. Once the shielding sleeve surrounding the rotor wears and cracks, it will cause leakage of hazardous media, leading to serious safety and environmental accidents.

[0004] To address the issue of axial movement, existing technologies commonly employ a system of axial thrust bearings. For example, Chinese Patent CN104791257B discloses an improved structure device for a permanent magnet bottling pump, which attempts to bidirectionally limit the rotor's axial movement by using a system consisting of an inlet thrust ring, an impeller thrust bearing, and a rear cover thrust ring. During normal operation, hydrodynamic forces couple the bearing surface on one side of the rotor to the inlet thrust ring; during start-up, shutdown, or sudden changes in operating conditions, the other side of the rotor couples to the rear cover thrust ring, thereby limiting axial displacement within a predetermined safety clearance.

[0005] However, the axial thrust bearing system in this design is highly susceptible to wear. To ensure corrosion and wear resistance, the thrust ring and bearing are typically made of hard ceramic materials such as silicon carbide and alumina. Nevertheless, under conditions of pump start-up and shutdown, sudden load changes, or the presence of trace particles in the medium, it is difficult to maintain a complete liquid film lubrication between the thrust surfaces, leading to frequent boundary friction or even dry friction, resulting in unavoidable wear. With accumulated operating time, wear gradually increases the axial clearance, not only compromising operational stability but also significantly increasing the risk of catastrophic leakage due to the wear of the shielding sleeve. Summary of the Invention

[0006] To address the shortcomings of existing technologies, the purpose of this invention is to provide a rigid double-support magnetic pump. The technical problem this invention aims to solve is to overcome the problems of poor rotor axial stability, low operational reliability, and the risk of leakage due to wear and tear of the shielding sleeve in existing magnetic pumps caused by the easy wear of the axial thrust bearing system. The invention provides a rigid double-support magnetic pump that can achieve rigid axial constraint of the rotor, significantly reduce wear, and ensure long-term safe and stable operation.

[0007] The objective of this utility model can be achieved through the following technical solution: A rigid double-support magnetic pump includes a motor housing and a pump housing fixedly connected. A rotor assembly and a stator assembly are disposed within the motor housing. An impeller is disposed within the pump housing. The rotor assembly is enclosed by a rotor shielding sleeve, and the stator assembly is enclosed by a stator shielding sleeve. The rotor shielding sleeve is located within a recessed cavity of the stator shielding sleeve. A stator shielding sleeve and a support partition are fixedly connected between the motor housing and the pump housing. A fixing hole is provided within the support partition, and a fixing groove is provided within the stator shielding sleeve. A first rotating component is fixedly disposed within the fixing groove, and a second rotating component is fixedly disposed within the fixing hole. A support shaft is rotatably connected between the first and second rotating components. The rotor shielding sleeve is fixedly disposed on the outer circumference of the support shaft, and the support shaft is fixedly connected to the impeller.

[0008] Furthermore, a stepped groove is formed at the fixed connection between the motor housing and the pump housing, and the outer peripheral ends of the support partition and the stator shield sleeve are embedded in the stepped groove. A first sealing element and a second sealing element are sequentially arranged along the axial direction between the stator shield sleeve, the support partition and the stepped groove.

[0009] Furthermore, the support partition has a first convex ring portion and a second convex ring portion protruding from both sides along the axial direction. The outer circumferential diameter of the first convex ring portion is the same as the outer circumferential diameter of the support partition, and the outer circumferential diameter of the second convex ring portion is smaller than the outer circumferential diameter of the support partition. The stator shield sleeve has a third convex ring portion protruding towards the support partition. A first sealing element is provided between the third convex ring portion and the first convex ring portion, and a second sealing element is provided between the second convex ring portion and the stepped groove.

[0010] Furthermore, the first and third convex rings abut against each other to create a passageway between the two end faces of the support partition and the stator shield sleeve.

[0011] Furthermore, a support sealing gasket is provided between the support partition and the stepped groove, and the support sealing gasket is sleeved on the outer periphery of the second convex ring.

[0012] Furthermore, the stator shield sleeve has a supporting convex ring protruding towards the supporting partition, and the outer peripheral surface of the supporting partition abuts against the inner peripheral surface of the supporting convex ring.

[0013] Furthermore, the supporting partition covers the cavity opening, and the supporting partition protrudes towards the cavity to form a fixing column. The fixing column is provided with an axially penetrating fixing hole. The supporting shaft passes through the fixing hole and is fixed to the impeller. The impeller is axially opposite to the pump casing inlet.

[0014] Furthermore, a shaft support column is formed on the side of the stator shield sleeve facing away from the cavity opening, and the fixing groove is opened in the shaft support column, and its bottom wall has a closed structure.

[0015] Furthermore, an integral metal plate is embedded inside the supporting partition and the fixing column, and the metal plate is integrally formed with the supporting partition and the fixing column by injection molding.

[0016] Furthermore, the supporting partition is provided with a first through hole that extends axially, and the metal plate is provided with a second through hole that is aligned with the first through hole. The diameter of the second through hole is larger than the diameter of the first through hole, and the first through hole is always in communication with the cavity.

[0017] Compared with existing technologies, the technical advantages of this invention are as follows: First, this invention constructs a high-rigidity, low-deformation main shaft frame through a supporting shaft, a first rotating component, a second rotating component, a fixed groove, a supporting partition, and fixed holes. This frame directly transmits the axial thrust generated by the impeller as a static load to the supporting partition and pump casing, rather than relying on dynamic friction to offset the force. This design forms a strong axial constraint on the rotor system, limiting axial displacement to a very small bearing clearance, thereby greatly suppressing harmful axial movement. This significantly reduces vibration and noise during pump operation, avoids the risk of impact between the rotor and stationary components such as the pump cover or shielding sleeve, and ensures smooth and reliable operation. Simultaneously, by reducing axial friction, it reduces wear on the thrust bearing system, extends the pump's service life, and reduces the safety risk of hazardous media leakage due to shielding sleeve wear. Second, this invention also comprises a flexible boundary system consisting of a supporting sealing gasket, a first sealing element, and a second sealing element, which works in conjunction with the aforementioned rigid main shaft frame. The rigid frame bears the main axial force, ensuring the precise positioning of the core rotor; the flexible system absorbs thermal deformation, assembly stress, and internal stress caused by changes in operating conditions, releasing these stresses without affecting the stability of the core frame. This combination of rigidity and flexibility ensures structural robustness while providing necessary adaptability, enhancing the pump's ability to adapt to different operating conditions such as start-up and shutdown, sudden load changes, or temperature variations, further strengthening the system's long-term operational reliability and sealing integrity. Attached Figure Description

[0018] Figure 1 This is a cross-sectional view of the present invention.

[0019] Figure 2 This is an enlarged view of section A of this utility model.

[0020] Figure 3 This is a partial sectional view of the present invention.

[0021] Drawing number markings: 1. Pump casing; 2. Stator shielding sleeve; 21. Cavity; 211. Fixing groove; 22. Third convex ring; 23. Supporting convex ring; 24. Shaft support column; 3. Stator assembly; 4. Supporting shaft; 5. Rotor shielding sleeve; 6. Rotor assembly; 7. Supporting partition; 71. Fixing column; 72. Fixing hole; 73. Metal plate; 731. Second through hole; 74. First through hole; 75. First convex ring; 76. Second convex ring; 81. First rotating component; 82. Second rotating component; 9. Impeller; 10. Inlet; 11. Stepped groove; 12. Motor casing; 101. First seal; 102. Second seal; 103. Supporting sealing gasket; 104. Passage clearance. Detailed Implementation

[0022] The following are specific embodiments of the present invention, which are described in conjunction with the accompanying drawings. However, the present invention is not limited to these embodiments.

[0023] It should be noted that the descriptions of "up", "down", "left", "right", "top", "bottom", etc. in this utility model are defined based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device must be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0024] according to Figures 1 to 3 As shown, this utility model provides a rigid double-support magnetic pump, mainly comprising a motor housing 12 and a pump housing 1 fixedly connected. A rotor assembly 6 and a stator assembly 3 are disposed within the motor housing 12, and an impeller 9 is disposed within the pump housing 1. The rotor assembly 6 is enclosed by a rotor shielding sleeve 5, and the stator assembly 3 is enclosed by a stator shielding sleeve 2. The stator shielding sleeve 2 has a cavity 21, within which the rotor shielding sleeve 5 is located, thereby achieving magnetic coupling transmission between the rotor and the stator. The stator shielding sleeve 2 can be a separate component or an integrally formed piece.

[0025] The motor housing 12 and the pump housing 1 are fixedly connected by bolts or other fasteners, forming a stepped groove 11 at the connection. The outer periphery of the support partition 7 and the stator shield sleeve 2 is embedded in this stepped groove 11 to achieve axial positioning and sealing. The support partition 7 and the stator shield sleeve 2 are fixedly connected, together forming the static support frame of the pump. The pump housing 1, the support partition 7, the stator shield sleeve 2, and the motor housing 12 are connected and fixed in sequence.

[0026] A through-hole 72 is provided in the support partition 7. A shaft support column 24 is formed by the bottom protrusion of the cavity 21 of the stator shield sleeve 2. A fixing groove 211 is provided in the shaft support column 24, and the bottom wall of the fixing groove 211 is a closed structure. The fixing groove 211 is always in communication with the cavity 21. A first rotating member 81 is fixedly installed in the fixing groove 211, and a second rotating member 82 is fixedly installed in the fixing hole 72. A support shaft 4 is rotatably connected between the first rotating member 81 and the second rotating member 82. The rotor shield sleeve 5 is fixedly installed on the outer periphery of the support shaft 4. One end of the support shaft 4 passes through the fixing hole 72 and is fixedly connected to the impeller 9. The impeller 9 is axially opposite to the inlet 10 of the pump casing 1, so that the fluid power generated when the impeller 9 rotates directly acts on the medium in the inlet 10. The axial force of the medium entering the inlet 10 acts directly on the support partition 7, avoiding direct impact on the rotor shield sleeve 5.

[0027] The support partition 7 has a first convex ring portion 75 and a second convex ring portion 76 protruding from both sides along the axial direction. The outer diameter of the first convex ring portion 75 is the same as the outer diameter of the support partition 7, while the outer diameter of the second convex ring portion 76 is smaller than the outer diameter of the support partition 7. The stator shield sleeve 2 has a third convex ring portion 22 protruding towards the support partition 7. A first sealing element 101 and a second sealing element 102 are sequentially arranged axially between the stator shield sleeve 2, the support partition 7, and the stepped groove 11. That is, the first sealing element 101 is arranged between the third convex ring portion 22 and the first convex ring portion 75, and the second sealing element 102 is arranged between the second convex ring portion 76 and the stepped groove 11. The first convex ring portion 75 and the third convex ring portion 22 abut against each other, forming a passage gap 104 between the two end faces of the support partition 7 and the stator shield sleeve 2. This gap allows a small amount of fluid to pass through for lubrication and cooling, while avoiding hard contact.

[0028] A support sealing gasket 103 is also provided between the support partition 7 and the stepped groove 11. The support sealing gasket 103 is sleeved on the outer periphery of the second convex ring 76 to further enhance the sealing effect and absorb assembly stress.

[0029] The stator shielding sleeve 2 also has a supporting protruding ring 23 protruding towards the supporting partition 7. The outer peripheral surface of the supporting partition 7 abuts against the inner peripheral surface of the supporting protruding ring 23, providing radial support and centering, and ensuring the concentricity of the supporting partition 7 and the stator shielding sleeve 2.

[0030] The support partition 7 covers the opening of the cavity 21 and protrudes towards the cavity 21 to form a fixing post 71, into which a fixing hole 72 is formed. The support shaft 4 passes through the fixing hole 72 and is fixed to the impeller 9. To enhance the structural rigidity of the support partition 7 and the fixing post 71, an integral metal plate 73 is embedded inside the support partition 7 and the fixing post 71. The metal plate 73 is integrally formed with the support partition 7 and the fixing post 71 through injection molding, forming a composite structure that effectively resists deformation and load.

[0031] The support partition 7 is provided with a first through hole 74 that extends axially, and the metal plate 73 is provided with a second through hole 731 that is aligned with the first through hole 74. The diameter of the second through hole 731 is larger than the diameter of the first through hole 74. The first through hole 74 is always connected to the cavity 21, allowing the medium to circulate and flow, which is used for lubricating the bearing and dissipating heat, while balancing the pressure.

[0032] During pump operation, the motor-driven rotor assembly 6 drives the support shaft 4 and impeller 9 to rotate via magnetic coupling. The axial thrust generated by the impeller 9 is transmitted to the first rotating component 81 and the second rotating component 82 through the support shaft 4. Since the first rotating component 81 and the second rotating component 82 are respectively fixed to the stator shielding sleeve 2 and the support partition 7, and the support partition 7 and the stator shielding sleeve 2 are rigidly fixed through the motor housing 12 and the pump housing 1, the axial thrust is directly transmitted to the pump housing 1 and the motor housing 12 as a static load, rather than relying on dynamic friction. This design achieves rigid axial constraint on the rotor system, limiting axial displacement within the bearing clearance and effectively suppressing axial movement. At the same time, the flexible boundary system composed of the first seal 101, the second seal 102, and the support sealing gasket 103 can absorb thermal deformation and assembly stress, ensuring sealing integrity without affecting the stability of the core rigid frame.

[0033] The above embodiments are merely preferred embodiments of the present utility model and are not intended to limit the scope of protection of the present utility model. Therefore, all equivalent changes made to the structure, shape, and principle of the present utility model should be covered within the scope of protection defined by the claims of the present utility model.

Claims

1. A rigid double-supported magnetic pump, comprising a motor housing (12) and a pump housing (1) fixedly connected, wherein a rotor assembly (6) and a stator assembly (3) are disposed within the motor housing (12), and an impeller (9) is disposed within the pump housing (1), wherein the rotor assembly (6) is enclosed by a rotor shielding sleeve (5), and the stator assembly (3) is enclosed by a stator shielding sleeve (2), wherein the rotor shielding sleeve (5) is located within a cavity (21) of the stator shielding sleeve (2), characterized in that: The stator shield sleeve (2) and the support partition (7) are fixedly connected between the motor housing (12) and the pump housing (1). The support partition (7) is provided with a fixing hole (72). The stator shield sleeve (2) is provided with a fixing groove (211). A first rotating component (81) is fixedly installed in the fixing groove (211). A second rotating component (82) is fixedly installed in the fixing hole (72). The first rotating component (81) and the second rotating component (82) are rotatably connected to the support shaft (4). The rotor shield sleeve (5) is fixedly installed on the outer periphery of the support shaft (4). The support shaft (4) is fixedly connected to the impeller (9).

2. The rigid double-support magnetic pump according to claim 1, characterized in that: A stepped groove (11) is formed at the fixed connection between the motor housing (12) and the pump housing (1). The outer peripheral ends of the support partition (7) and the stator shield sleeve (2) are embedded in the stepped groove (11). A first sealing element (101) and a second sealing element (102) are arranged sequentially along the axial direction between the stator shield sleeve (2), the support partition (7) and the stepped groove (11).

3. A rigid double-support magnetic pump according to claim 2, characterized in that: The support partition (7) has a first protruding ring (75) and a second protruding ring (76) protruding from both sides along the axial direction. The outer diameter of the first protruding ring (75) is the same as the outer diameter of the support partition (7), and the outer diameter of the second protruding ring (76) is smaller than the outer diameter of the support partition (7). The stator shield sleeve (2) has a third protruding ring (22) protruding towards the support partition (7). A first sealing element (101) is provided between the third protruding ring (22) and the first protruding ring (75), and a second sealing element (102) is provided between the second protruding ring (76) and the stepped groove (11).

4. A rigid double-support magnetic pump according to claim 3, characterized in that: The first convex ring (75) and the third convex ring (22) abut against each other to create a passage gap (104) between the two end faces of the support partition (7) and the stator shield sleeve (2).

5. A rigid double-support magnetic pump according to claim 3, characterized in that: A support sealing gasket (103) is provided between the support partition (7) and the stepped groove (11), and the support sealing gasket (103) is sleeved on the outer periphery of the second convex ring (76).

6. A rigid double-support magnetic pump according to claim 1, characterized in that: The stator shield sleeve (2) has a supporting protruding ring (23) protruding towards the supporting partition (7), and the outer peripheral surface of the supporting partition (7) abuts against the inner peripheral surface of the supporting protruding ring (23).

7. A rigid double-support magnetic pump according to any one of claims 1 to 6, characterized in that: The supporting partition (7) covers the opening of the cavity (21). The supporting partition (7) protrudes towards the cavity (21) to form a fixing column (71). The fixing column (71) is provided with an axially penetrating fixing hole (72). The supporting rotating shaft (4) passes through the fixing hole (72) and is fixed to the impeller (9). The impeller (9) is axially opposite to the inlet (10) of the pump casing (1).

8. A rigid double-support magnetic pump according to claim 7, characterized in that: The stator shield sleeve (2) has a axial support column (24) protruding from the side opposite to the opening of the concave cavity (21). The fixing groove (211) is opened in the axial support column (24) and its bottom wall has a closed structure.

9. A rigid double-support magnetic pump according to any one of claims 1 to 6, characterized in that: An integral metal plate (73) is embedded inside the supporting partition (7) and the fixing column (71). The metal plate (73) is integrally formed with the supporting partition (7) and the fixing column (71) by injection molding.

10. A rigid double-support magnetic pump according to claim 9, characterized in that: The supporting partition (7) is provided with a first through hole (74) that extends through the axis, and the metal plate (73) is provided with a second through hole (731) that is aligned with the first through hole (74). The diameter of the second through hole (731) is larger than the diameter of the first through hole (74), and the first through hole (74) is always connected to the cavity (21).

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