Magnetic liquid coupling suspension mechanical pump

Abstract

The invention provides a magnetic liquid coupling suspension mechanical pump which comprises a pump cover, an impeller assembly, an end cover, a machine shell and a rotor assembly. The center area of the machine shell is concave inwards to form an inner shell cavity. The end cover is located between the pump cover and the machine shell, and a center hole is formed in the end cover. The rotor assembly is installed in the inner shell cavity. A wheel shaft of the impeller assembly penetrates through the center hole to be fixedly connected with the rotor assembly. A first gap exists between the top of the rotor assembly and the end cover, a second gap exists between the bottom of the rotor assembly and the bottom wall of the inner shell cavity, and the sum of the first gap and the second gap is set to range from 0.05 mm to 10.0 mm. By optimizing the gaps between the rotor assembly and the end cover and between the rotor assembly and the bottom wall of the inner shell cavity, the supporting force of the mechanical pump is remarkably enhanced, the suspension performance is more stable, the optimized gap design not only improves the synergistic effect of fluid dynamic performance and electromagnetic force, but also reduces mechanical friction and vibration, and the service life of the mechanical pump is prolonged. And high efficiency, low noise and long service life of the mechanical pump during high-rotating-speed operation are ensured.

Description

Technical Field

[0001] The present invention belongs to the field of mechanical pumps, and particularly relates to a magnetic fluid coupling suspension mechanical pump. Background Art

[0002] With the rapid development of AI servers, new energy, data centers, etc., the integration of electronic devices is getting higher and higher, and the heat generation per unit area is getting larger and larger. The traditional air-cooled heat dissipation scheme cannot meet the higher system requirements, and the development and large-scale application of the active liquid-cooled heat dissipation scheme have become inevitable. The mechanical pump is the core component of the liquid-cooled heat dissipation system, and its performance and reliability directly determine the performance and reliability of the system. In addition, as an important research direction of microelectromechanical systems, mechanical pumps are also widely used in fields such as chemical transportation systems, special pumping systems, and medical equipment.

[0003] The mechanical pumps applied in the liquid-cooled heat dissipation industry are contact bearing pumps, which have mechanical friction losses during high-speed rotation, resulting in a working life of generally 2 to 3 years for mechanical pumps, which cannot meet the usage requirements of application scenarios with high reliability requirements (for example, the service life of liquid-cooled products in data centers and charging piles is up to 10 to 15 years). The key to solving this problem lies in solving bearing wear. Among them, the magnetic suspension bearing technology is a direction, and researchers have designed different forms of suspension mechanical pumps using the principle of magnetic levitation or the principle of hydraulic levitation. Among them, the magnetic suspension bearing needs to use a sensor to capture the position of the rotor in real time and feedback the position signal to the auxiliary coil, so as to generate a balancing force to keep the rotor in a suspended state at all times. The system structure of this scheme is complex, and the system loss is large, with serious heat generation, which is not suitable for the liquid-cooled heat dissipation field. The hydraulic suspension technology can make the rotor achieve full-degree-of-freedom suspension through the hydraulic action of the fluid inside the pump.

[0004] In the current hydraulic suspension technology or magnetic fluid hybrid suspension technology in the industry, the fluid needs to be introduced into the motor by using a pressure difference, so as to generate a hydraulic pressure in the motor to provide a suspension effect. Therefore, it is particularly important to improve sufficient hydraulic pressure to ensure its suspension effect.

[0005] In addition, the existing schemes mostly adopt open impellers so that the liquid in the motor can smoothly enter the central low-pressure area of the pump inlet. However, the blade roots of the open impellers have low strength, and the blades are prone to force deformation and failure during high-speed or high-performance operation of the pump, and the blade gap leakage of the open impellers is large, resulting in low hydraulic efficiency.

[0006] In summary, there is a need for an impeller that can allow the fluid in the central low-pressure area of the pump inlet to enter the motor, while ensuring that the blade roots have sufficient strength, and can reduce the leakage of the tip clearance and improve the hydraulic efficiency. Summary of the Invention

[0007] In view of the above-mentioned disadvantages of the prior art, the purpose of the present invention is to provide a magnetic fluid coupling suspension mechanical pump, so as to solve the problems that in the existing solutions, an open impeller is mostly used to enable the liquid in the motor to smoothly enter the central low-pressure area of the pump inlet. However, the blade root strength of the open impeller is relatively low, and the blades are prone to force deformation and failure during high-speed or high-performance operation of the pump. In addition, the blade gap leakage of the open impeller is relatively large, resulting in low hydraulic efficiency.

[0008] To achieve the above and other related purposes, the present invention provides a magnetic fluid coupling suspension mechanical pump, including: a pump cover, an impeller assembly, an end cover, a housing, and a rotor assembly;

[0009] The central area of the housing is recessed to form an inner housing cavity;

[0010] The end cover is located between the pump cover and the housing, and a central hole is provided on the end cover;

[0011] The rotor assembly is installed in the inner housing cavity;

[0012] The wheel shaft of the impeller assembly passes through the central hole and is fixedly connected to the rotor assembly;

[0013] Wherein, there is a first gap between the top of the rotor assembly and the end cover, and a second gap between the bottom of the rotor assembly and the bottom wall of the inner housing cavity. The sum of the first gap and the second gap is set to be 0.05 mm to 10.0 mm.

[0014] In an embodiment of the present invention, a circumferential hole is further provided on the end cover, and the through hole of the wheel disc of the impeller assembly is communicated with the circumferential hole to form a fluid passage from the pump cavity inside the pump cover to the inner housing cavity, so that the low-pressure liquid in the pump cavity can flow into the wheel disc through hole through the fluid passage and then into the first gap, the second gap, and the gap between the rotor assembly and the side wall of the inner housing cavity, so as to form a liquid pressure to support the rotor assembly against the cavity wall of the inner housing cavity and the periphery of the rotor assembly.

[0015] In an embodiment of the present invention, the shaft has a flat position structure, including a single flat position, a double flat position, or a multi-flat position, and the flat position structure is connected to the rotor assembly by interference fit.

[0016] In an embodiment of the present invention, the impeller assembly further includes blades and a wheel disc,

[0017] The wheel disc is arranged at one end of the wheel shaft;

[0018] The blades are arranged on the wheel disc;

[0019] The ratio range of the outer diameter of the wheel disc to the outer diameter of the blades is 0.1 to 1.5.

[0020] In one embodiment of the present invention, a plurality of through holes are provided on the roulette wheel and are evenly distributed along the circumferential direction of the roulette wheel.

[0021] In one embodiment of the present invention, a flow guiding boss is provided at the bottom of the roulette wheel, and the flow guiding boss forms a stepped fluid acceleration channel along the direction towards the central position of the roulette wheel.

[0022] In one embodiment of the present invention, the roulette wheel is of a semi-closed or fully-closed structure.

[0023] In one embodiment of the present invention, the impeller assembly further includes blades and a hub. The hub is fixedly connected to the wheel shaft, and the blades are connected to the hub.

[0024] In one embodiment of the present invention, a plurality of fluid passages are formed around the rotor, including:

[0025] A first fluid passage, where liquid flows into the first gap between the rotor assembly and the end cover through the through holes and circumferential holes on the roulette wheel;

[0026] A second fluid passage, where liquid flows downward through the gap between the wheel shaft and the inner hole of the rotor assembly;

[0027] A third fluid passage, where liquid is in the second gap between the rotor assembly and the bottom of the inner cavity of the casing and is centrifugally accelerated in the gap;

[0028] A fourth fluid passage, where liquid flows back to the first fluid passage through the gap between the rotor assembly and the wall surface of the inner cavity of the casing.

[0029] In one embodiment of the present invention, the liquid film in the fourth fluid passage forms a radial support for the rotor assembly, and at the same time, the axial suspension of the rotor assembly is achieved by the combined action of magnetic pulling force and fluid axial force.

[0030] In one embodiment of the present invention, a spiral return groove is provided between the rotor assembly and the inner wall of the casing, and the pitch of the spiral return groove gradually decreases along the liquid flow direction for guiding the liquid to form a vortex liquid film.

[0031] The present invention has the following beneficial effects:

[0032] The existence of the first gap and the second gap in the present invention ensures that a stable liquid film can be formed around the rotor assembly. The formation of the liquid film is crucial for the radial and axial support of the rotor assembly, which can effectively reduce mechanical friction and extend the service life of the mechanical pump. At the same time, the design of the gap optimizes the fluid flow path, ensuring that the liquid can flow smoothly around the rotor assembly, reducing energy loss, and improving the hydraulic efficiency of the pump. When the sum of the first gap and the second gap is set to 0.05 mm to 10.0 mm, the best hydrodynamic performance and mechanical stability can be achieved. If the gap is too small, mechanical friction will increase, while if the gap is too large, liquid leakage and suspension stability will decline. By optimizing the gaps between the rotor assembly and the end cover and the bottom wall of the inner shell cavity, the supporting force of the mechanical pump is significantly enhanced, and the suspension performance is more stable. The optimized gap design not only improves the synergistic effect of hydrodynamic performance and electromagnetic force, but also reduces mechanical friction and vibration, ensuring the high efficiency, low noise, and long life of the mechanical pump during high-speed operation.

[0033] Through the structural design of the disk in the present invention, the contact area between the blade root and the disk is increased, significantly improving the mechanical strength of the blade, preventing blade deformation and failure caused by high-speed or high-performance operation, enhancing the reliability of the impeller. At the same time, through the optimized design of the ratio of the outer diameter of the disk to the outer diameter of the blade, the leakage of the tip clearance is reduced, the hydraulic efficiency of the pump is improved, which is beneficial to the increase of liquid pressure, enabling the rotor assembly to achieve full-degree-of-freedom suspension, avoiding mechanical friction, extending the service life of the mechanical pump, and meeting the requirements of high-reliability application scenarios. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required for describing the embodiments will be briefly introduced below. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0035] Figure 1 It is a schematic structural diagram of the present invention in one embodiment.

[0036] Figure 2 It is a schematic structural diagram of the end cover of the present invention in one embodiment.

[0037] Figure 3 It is a schematic structural diagram of the semi-closed impeller assembly of the present invention in one embodiment.

[0038] Figure 4 It is a schematic structural diagram of the fully-closed impeller assembly of the present invention in one embodiment.

[0039] Figure 5 It is a schematic diagram of the fluid channel of the inner shell cavity of the present invention in one embodiment.

[0040] Figure 6 It is a schematic diagram of the axial force on the rotor in an embodiment of the present invention.

[0041] Figure 7 It is a schematic diagram of the structure of the impeller assembly in another embodiment of the present invention.

[0042] Label description:

[0043] 1. Pump cover; 2. Impeller assembly; 2a. Blade; 2b. Disk; 2b'. Fully enclosed disk; 2c. Shaft; 2d. Disk through-hole; 3. Sealing ring; 4. End cover; 5. Housing; 6. Stator skeleton; 7. Coil winding; 8. Stator core; 9. Rotor sleeve; 10. Rotor; 11. Bush; 12. Driving plate; 13. Rear cover. Detailed implementation manners

[0044] The following uses specific specific examples to illustrate the implementation manners of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. The present invention can also be implemented or applied through other different specific implementation manners. Various details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of the present invention.

[0045] It should be noted that the illustrations provided in this embodiment only schematically illustrate the basic concept of the present invention. Therefore, only the components related to the present invention are shown in the drawings, rather than being drawn according to the number, shape, and size of the components in actual implementation. The type, quantity, and ratio of each component in actual implementation can be arbitrarily changed, and the layout type of its components may also be more complex.

[0046] Please refer to Figures 1 to 6As shown in the figure, the present invention provides a magnetic fluid coupling suspension mechanical pump and an impeller assembly to solve the problem that existing solutions mostly adopt open impellers so that the liquid in the motor can smoothly enter the central low-pressure area of the pump inlet. However, the blade roots of the open impellers have low strength, and the blades are prone to force deformation and failure during high-speed or high-performance operation of the pump. In addition, the blade clearance leakage of the open impellers is large, resulting in low hydraulic efficiency. In this embodiment, the mechanical pump includes a pump cover 1, an impeller assembly 2, a sealing ring 3, an end cover 4, a casing 5, a stator skeleton 6, a coil winding 7, a stator core 8, a rotor sleeve 9, a rotor 10, a shaft sleeve 11, a driving plate 12, and a rear cover 13. The pump cover 1 is provided with a water inlet port 1a and a water outlet port 1b, and the internal space serves as a pump chamber. The water inlet port 1a and the water outlet port 1b are respectively communicated with the pump chamber. The pump cover 1 is made of high-strength aluminum alloy or engineering plastic, and its surface is precision machined to ensure the fitting accuracy with the end cover 4 and the casing 5. A sealing groove is provided on the pump cover 1, and the sealing ring 3 is placed in the sealing groove. The pump cover and the casing are locked by screws to form a compression seal for the sealing ring, ensuring the sealing performance between the end cover 4 and the pump cover 1 and preventing liquid leakage.

[0047] Please refer to Figure 1 and Figure 2 As shown in the figure, in this embodiment, the end cover 4 is located between the pump cover 1 and the casing 5 and is connected to the casing by clearance fit. The end cover is provided with a circumferential hole 4b and a central hole 4a. The central hole 4a is used to connect with the impeller assembly 2, and the circumferential hole 4b is communicated with the pump chamber to form a fluid channel, ensuring that the low-pressure liquid in the pump chamber can enter the inner casing cavity and providing hydraulic pressure for the rotor assembly. The end cover is made of high-strength aluminum alloy, and its surface is precision machined to ensure the fitting accuracy with the pump cover and the casing.

[0048] Please refer to Figure 1 and Figure 2 As shown in the figure, in this embodiment, the central area of the casing 5 is recessed to form an inner casing cavity, and the casing and the rear cover 13 enclose an outer casing cavity. The inner casing cavity is used to accommodate the rotor assembly, and the outer casing cavity is used to accommodate the stator skeleton 6, the coil winding 7, the stator core 8, and the driving plate 12. The casing 5 is made of engineering plastic and is integrally formed by injection molding to ensure structural strength and lightweight design. In this embodiment, the casing provides support for the rotor assembly and, through the separation of the inner casing cavity and the outer casing cavity, ensures the independence of the electromagnetic field and the fluid.

[0049] Please refer to Figure 1 and Figure 2As shown, in this embodiment, the stator assembly includes a stator frame 6, a coil winding 7, and a stator core 8. The stator frame 6 is an insulating structure, installed at the upper and lower ends of the stator core 8, separating the coil winding 7 and the stator core 8. The coil winding 7 is wound around the stator frame 6. The stator frame 6 is made of high-strength insulating material, the coil winding 7 is wound with high-strength enameled wire, and the stator core 8 is stacked by multiple magnetic conductive sheet materials. The stator assembly generates an electromagnetic field, interacts with the magnetic field of the rotor assembly, forms a magnetic pulling force, and realizes the suspension of the rotor assembly.

[0050] Please refer to Figure 1 , Figure 3 and Figure 4 As shown, in this embodiment, the rotor assembly includes a rotor sleeve 9, a rotor 10, and a bushing 11. The rotor sleeve 9 is located outside the rotor 10, and the bushing 11 is located inside the rotor 10. They are in clearance fit with each other and fixed by glue. In this embodiment, the surface of the rotor 10 is provided with an anti-corrosion coating. The rotor sleeve 9 and the bushing 11 are made of high-strength engineering plastic or aluminum alloy. The rotor 10 is a magnetic material, and multiple permanent magnets are embedded inside. The rotor assembly generates a magnetic pulling force under the action of the electromagnetic field, and cooperates with the hydraulic pressure to realize full-degree-of-freedom suspension.

[0051] Please refer to Figure 1 , Figure 3 and Figure 4 As shown, in this embodiment, there is a first gap between the top of the rotor assembly and the end cover 4, and a second gap between the bottom of the rotor assembly and the bottom wall of the inner shell cavity. The sum of the first gap and the second gap is set to be 0.05 mm to 10.0 mm. The existence of the first gap and the second gap ensures that the liquid can form a stable liquid film around the rotor assembly. The formation of the liquid film is crucial for the radial and axial support of the rotor assembly, which can effectively reduce mechanical friction and extend the service life of the mechanical pump. At the same time, the design of the gap optimizes the flow path of the fluid, ensures that the liquid can flow smoothly around the rotor assembly, reduces energy loss, and improves the hydraulic efficiency of the pump. For example, the sum of the gaps can be set to 0.05 mm, 0.2 mm, 1 mm, 3 mm, 7 mm, 10 mm, and the magnitudes of the axial suspension forces under the sum of each gap are shown in Table 1.

[0052] Table 1 Comparison table of the sum of gaps and the magnitudes of axial suspension rates

[0053]

[0054] It is understandable that when the sum of the first gap and the second gap is set to be 0.05 mm to 10.0 mm, the best hydrodynamic performance and mechanical stability can be achieved. If the gap is too small, it will lead to an increase in mechanical friction, while if the gap is too large, it will result in liquid leakage and a decrease in suspension stability. By optimizing the gaps between the rotor assembly and the end cover and the bottom wall of the inner shell cavity, the supporting force of the mechanical pump is significantly enhanced, and the suspension performance is more stable. The optimized gap design not only improves the synergistic effect of hydrodynamic performance and electromagnetic force, but also reduces mechanical friction and vibration, ensuring the high efficiency, low noise and long life of the mechanical pump during high-speed operation.

[0055] Please refer to Figure 1 、 Figure 3 and Figure 4 As shown, in this embodiment, the impeller assembly 2 includes blades 2a, a wheel disc 2b and a wheel shaft 2c. The wheel disc 2b is arranged at one end of the wheel shaft 2c, and the blades 2a are arranged on the wheel disc 2b. The blades 2a, the wheel disc 2b and the wheel shaft 2c can be an integrally formed structure. A plurality of wheel disc through holes 2d are arranged on the wheel disc 2b, which are evenly distributed along the circumferential direction of the wheel disc 2b, ensuring that the liquid can uniformly flow into the periphery of the rotor assembly through the wheel disc through holes 2d, forming a stable liquid pressure to support the rotor assembly. It is understandable that the structural design of the wheel disc 2b increases the contact area between the blade root and the wheel disc, significantly improving the mechanical strength of the blades, preventing blade deformation and failure caused by high-speed or high-performance operation, enhancing the reliability of the impeller, and the uniform distribution of the wheel disc through holes 2d ensures that the liquid uniformly flows into the periphery of the rotor assembly, forming a stable liquid pressure and enhancing the suspension performance. In this embodiment, the wheel shaft 2c is a flat structure, including a single flat position, a double flat position or a multi-flat position, and is fixedly connected to the rotor assembly by interference fit, ensuring the stability and accuracy of the connection. The interference fit between the wheel shaft 2c and the rotor assembly ensures the synchronous rotation of the impeller assembly and the rotor assembly, avoiding connection loosening caused by axial movement. The design of the flat structure ensures a more stable interference fit between the wheel shaft and the rotor assembly, avoiding connection loosening caused by axial movement, significantly enhancing the connection stability between the wheel shaft and the rotor assembly, and ensuring the reliability of the mechanical pump during high-speed operation.

[0056] Please refer to Figure 1 、 Figure 3 and Figure 4As shown, in this embodiment, the wheel disc 2b can be set as a semi-closed type, and of course, it can also be set as a fully closed structure wheel disc 2b', so as to increase the contact area between the blade root and the wheel disc structure, improve the mechanical strength of the blade root, prevent blade deformation failure caused by high-speed or high-performance operation, and improve the mechanical reliability of the impeller. Further, the outer diameter of the wheel disc 2b can be set to be greater than, less than or equal to the outer diameter of the blade 2a. Specifically, the ratio range of the outer diameter of the wheel disc 2b to the outer diameter of the blade 2a is 0.1-1.5. By optimizing the design, the tip clearance leakage is reduced, and the hydraulic efficiency of the pump is improved. A flow guiding boss is provided at the bottom of the wheel disc 2b. The flow guiding boss forms a stepped fluid acceleration channel along the direction towards the center position of the wheel disc 2b. The stepped fluid acceleration channel design of the flow guiding boss optimizes the fluid flow path, improves the formation efficiency of the liquid pressure, and enhances the suspension performance.

[0057] Please refer to Figure 7 As shown, in some other embodiments, the impeller assembly 2 includes a blade 2a', a hub 2b" and a shaft 2c. The hub 2b" is fixedly connected to the shaft 2c, and the blade 2a' is connected to the hub 2b". The impeller assembly 2 is press-fitted with the rotor assembly by interference fit. The interference press-fitting stroke can be accurately controlled by an electronic press or a servo press. The end cover 4 is located between the impeller assembly 2 and the rotor assembly, and the impeller assembly passes through the central hole of the end cover 4. It can be understood that the impeller assembly 2 can also be set as other forms of structures. For example, a traditional open impeller structure.

[0058] Please refer to Figure 1 、 Figure 5 and Figure 6As shown, in this embodiment, four main fluid channels are designed inside the mechanical pump, namely the first fluid channel, the second fluid channel, the third fluid channel, and the fourth fluid channel. The path of the first fluid channel is that the liquid flows into the gap between the rotor assembly and the end cover 4 through the through holes 2d in the disk and the circumferential holes 4b on the end cover 4. This channel provides an initial liquid pressure for the rotor assembly to ensure that the rotor assembly can quickly form a suspended state at startup. The number and diameter of the circumferential holes 4b are optimized to ensure that the liquid can flow evenly around the rotor assembly to form a stable liquid pressure. The path of the second fluid channel is that the liquid flows downward through the gap between the shaft 2c of the impeller assembly 2 and the inner hole of the rotor assembly. This channel provides liquid pressure for the bottom of the rotor assembly to ensure the suspension stability of the rotor assembly in the axial direction. The gap between the shaft 2c and the inner hole of the rotor assembly is precisely machined to ensure smooth liquid flow and reduce energy loss. The path of the third fluid channel is the gap in diameter between the rotor assembly and the inner shell cavity. The liquid is centrifugally accelerated in this path. Further, a diversion groove is provided at the bottom of the inner shell cavity of the housing 5 to optimize the liquid flow path and improve the formation efficiency of the liquid pressure. The path of the fourth fluid channel is that the liquid flows back to the first fluid channel through the gap between the rotor assembly and the wall surface of the inner shell cavity of the housing 5. This channel forms a circulating flow to ensure that the liquid can continuously provide liquid pressure for the rotor assembly and at the same time take away the heat generated during operation.

[0059] It can be understood that the liquid film in the fourth fluid channel forms a radial support for the rotor assembly, and at the same time, the axial suspension of the rotor assembly is realized by the combined action of the magnetic pulling force and the fluid axial force. The thickness of the liquid film is optimized through hydrodynamic design to ensure the stability of the rotor assembly during high-speed operation. Further, a spiral return groove is provided between the rotor assembly and the inner wall of the housing 5, and the pitch gradually decreases along the liquid flow direction. The design of the return groove optimizes the fluid flow path, reduces energy loss, and can guide the liquid to form a vortex liquid film to further optimize the fluid flow path and improve the suspension performance.

[0060] Please refer to Figure 1 、 Figure 5 and Figure 6As shown, in this embodiment, when the mechanical pump is operating, liquid flows into the pump chamber from the water inlet 1a. Most of the liquid flows out to the water outlet 1b after the impeller rotates and does work, and a small part of the liquid flows into the inner shell cavity through the through-holes 2d in the disk and the circumferential holes 4b in the end cover 4. The liquid forms a circulating flow through the first fluid channel, the second fluid channel, the third fluid channel, and the fourth fluid channel. The liquid forms a circulating flow through the four fluid channels to provide hydraulic pressure to support the rotor assembly. The rotor assembly realizes full-degree-of-freedom suspension through the coupling effect of hydraulic pressure and electromagnetic force. The overall design of the mechanical pump realizes full-degree-of-freedom suspension, avoids mechanical friction, extends the service life, meets the requirements of high-reliability application scenarios. The optimized fluid channel design and disk structure significantly improve the hydraulic efficiency of the pump, reduce the operating noise, and ensure the stability and reliability of the mechanical pump during high-speed or high-performance operation.

[0061] When the mechanical pump of the present invention operates at high speed, the mechanical strength of the impeller assembly is significantly improved, and no deformation failure phenomenon occurs at the blade root. The leakage of the tip clearance is reduced, the hydraulic efficiency is increased by about 15%, the rotor assembly realizes full-degree-of-freedom suspension, operates smoothly, has no mechanical friction, the noise is reduced by about 20 decibels, and the service life is extended to more than 10 years, meeting the requirements of high-reliability application scenarios.

[0062] The present invention provides a magneto-hydraulic coupled suspension mechanical pump. The existence of the first gap and the second gap ensures that the liquid can form a stable liquid film around the rotor assembly. The formation of the liquid film is crucial for the radial and axial support of the rotor assembly, can effectively reduce mechanical friction, and extend the service life of the mechanical pump. At the same time, the design of the gap optimizes the flow path of the fluid, ensures that the liquid can flow smoothly around the rotor assembly, reduces energy loss, and improves the hydraulic efficiency of the pump. When the sum of the first gap and the second gap is set to 0.05 mm to 10.0 mm, the best hydrodynamic performance and mechanical stability can be achieved. Too small a gap will lead to an increase in mechanical friction, while too large a gap will lead to liquid leakage and a decrease in suspension stability. By optimizing the gap between the rotor assembly and the end cover and the bottom wall of the inner shell cavity, the supporting force of the mechanical pump is significantly enhanced, and the suspension performance is more stable. The optimized gap design not only improves the synergistic effect of hydrodynamic performance and electromagnetic force, but also reduces mechanical friction and vibration, ensuring the high efficiency, low noise, and long life of the mechanical pump during high-speed operation.

[0063] The present invention provides a magnetic fluid coupling suspension mechanical pump. Through the structural design of the impeller, the contact area between the blade root and the impeller is increased, significantly enhancing the mechanical strength of the blade, preventing blade deformation and failure caused by high-speed or high-performance operation, improving the reliability of the impeller. At the same time, through the optimized design of the ratio of the outer diameter of the impeller to the outer diameter of the blade, the leakage of the tip clearance is reduced, the hydraulic efficiency of the pump is improved, which is beneficial to the improvement of the liquid pressure, enabling the rotor assembly to achieve full-degree-of-freedom suspension, avoiding mechanical friction, prolonging the service life of the mechanical pump, and meeting the requirements of high-reliability application scenarios.

[0064] The above-described embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that they can still modify the technical solutions recorded in the foregoing embodiments, or perform equivalent replacements for some of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions of the various embodiments of the present invention, and should all be included in the protection scope of the present invention.

[0065] Except for the technical features described in the specification, the remaining technical features are known to those skilled in the art. To highlight the innovative features of the present invention, the remaining technical features are not described herein again.

Claims

1. A magnetic fluid coupling suspension mechanical pump, characterized in that: include: A pump cover (1), an impeller assembly (2), an end cover (4), a casing (5) and a rotor assembly; The central area of ​​the housing (5) is concave to form an inner housing cavity; The end cover (4) is located between the pump cover (1) and the casing (5), and a center hole (4a) is provided on the end cover (4); The rotor assembly is installed in the inner shell cavity; The wheel shaft (2c) of the impeller assembly (2) passes through the central hole (4a) and is fixedly connected to the rotor assembly; There is a first gap between the top of the rotor assembly and the end cover, and a second gap between the bottom of the rotor assembly and the bottom wall of the inner shell cavity. The sum of the first gap and the second gap is set to 0.05 mm to 10.0 mm.

2. The magnetic liquid coupling suspension mechanical pump according to claim 1, characterized in that: The end cover (4) is also provided with a circumferential hole (4b), and the wheel disc through hole (2d) of the impeller assembly (2) is connected to the circumferential hole (4b), forming a fluid passage from the pump chamber inside the pump cover to the inner shell chamber, so that the low-pressure liquid in the pump chamber can flow through the fluid passage into the wheel disc through hole (2d) and into the first gap, the second gap and the gap between the rotor assembly and the side wall of the inner shell chamber, so as to form a liquid pressure to support the rotor assembly to enter the cavity wall of the inner shell chamber and the surroundings of the rotor assembly.

3. The magnetic liquid coupling suspension mechanical pump according to claim 1, characterized in that: The shaft (2c) is a flat structure, including a single flat, a double flat or a multi-flat structure, and the flat structure is connected to the rotor assembly through an interference fit.

4. The magnetic liquid coupling suspension mechanical pump according to claim 2, characterized in that: The impeller assembly further comprises blades (2a) and a wheel disc (2b). The wheel disc (2b) is arranged at one end of the wheel axle (2c); The blades (2a) are arranged on the wheel disc (2b); The ratio of the outer diameter of the wheel disc (2b) to the outer diameter of the blade (2a) is in the range of 0.1 to 1.

5.

5. The magnetic liquid coupling suspension mechanical pump according to claim 4, characterized in that: The wheel disc is provided with a plurality of wheel disc through holes (2d), which are evenly distributed along the circumference of the wheel disc (2b).

6. The magnetic liquid coupling suspension mechanical pump according to claim 4, characterized in that: A flow-guiding boss is provided at the bottom of the wheel disc (2b), and the flow-guiding boss forms a stepped fluid acceleration channel in a direction toward the center of the wheel disc (2b).

7. The magnetic liquid coupling suspension mechanical pump according to claim 5, characterized in that: The wheel disc (2b) is of a semi-enclosed or fully-enclosed structure.

8. The magnetic liquid coupling suspension mechanical pump according to claim 1, characterized in that: The impeller assembly (2) further comprises blades (2a') and a hub (2b"), wherein the hub (2b") is fixedly connected to the wheel shaft (2c), and the blades (2a') are connected to the hub (2b").

9. The magnetic liquid coupling suspension mechanical pump according to claim 3, characterized in that: A plurality of fluid passages are formed around the rotor, including: A first fluid channel, wherein the liquid flows into a first gap between the rotor assembly and the end cover (4) through the wheel disc through hole (2d) and the circumferential hole (4b); A second fluid channel, in which the liquid flows downward through the gap between the wheel shaft (2c) and the inner hole of the rotor assembly; A third fluid channel, in which the liquid is in a second gap between the rotor assembly and the bottom of the inner shell cavity of the casing (5), and is centrifugally accelerated in the gap; In the fourth fluid channel, the liquid flows back to the first fluid channel through the gap between the rotor assembly and the wall surface of the inner shell cavity of the casing (5).

10. The magnetic liquid coupling suspension mechanical pump according to claim 9, characterized in that: The liquid film in the fourth fluid channel forms radial support for the rotor assembly, and the axial suspension of the rotor assembly is achieved by the synergistic effect of the magnetic pulling force and the axial force of the fluid.

11. The magnetic liquid coupling suspension mechanical pump according to claim 9, characterized in that: A spiral reflux groove is provided between the rotor assembly and the inner wall of the casing (5), wherein the pitch of the spiral reflux groove gradually decreases along the flow direction of the liquid, and is used to guide the liquid to form a vortex liquid film.

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