High speed pump

Abstract

The application discloses a high-speed pump, which comprises a pump body, an internal cavity of the pump body, an open end of the internal cavity at a first end of the pump body, a liquid inlet end and a liquid outlet end of the pump body, a support at the first end of the pump body, an isolation sleeve at the first end and clamped between the pump body and the support, an impeller assembly in a space surrounded by the pump body and the isolation sleeve, the impeller assembly comprising an impeller and an inner magnetic assembly, an outer magnetic assembly in the support and located at an outer periphery of the isolation sleeve, outer magnets on the outer magnetic assembly and inner magnets on the inner magnetic assembly at least partially overlapping in an axial direction, a front cover plate on the pump body and located in the internal cavity, a cover plate channel on the front cover plate and communicating the liquid inlet end and a liquid inlet side of the impeller, the front cover plate and the impeller being arranged in the axial direction and capable of sliding in the axial direction relative to the pump body.

Description

Technical Field

[0001] This application belongs to the field of pump equipment technology, specifically relating to a high-speed pump. Background Technology

[0002] High-speed pumps are a type of centrifugal pump. Existing high-speed pumps typically contain rotating components such as shafts and bearings to support the impeller, resulting in a large axial and radial footprint, complex overall structure, and cumbersome installation. Therefore, it is necessary to improve the existing technology to overcome these shortcomings. Summary of the Invention

[0003] Therefore, the technical problem to be solved by this application is to provide a high-speed pump with a simple structure.

[0004] To solve the above-mentioned technical problems, this application provides a high-speed pump, the high-speed pump comprising: a pump body having a pump cavity formed inside, the pump cavity having an opening at a first end of the pump body, the pump body also having an inlet end and an outlet end communicating with the pump cavity; a support bracket disposed at the first end of the pump body; an isolation sleeve disposed at the first end, located inside the support bracket, and sandwiched between the pump body and the support bracket; and an impeller assembly disposed within the space enclosed by the pump body and the isolation sleeve, the impeller assembly including an impeller and a blade... The impeller is connected to an inner magnetic assembly; an outer magnetic assembly is disposed within the bracket and located on the outer periphery of the isolation sleeve, wherein the outer magnet on the outer magnetic assembly and the inner magnet on the inner magnetic assembly overlap at least partially in the axial direction to form a magnetic coupling transmission to drive the impeller to rotate; a front cover plate is disposed on the pump body and located within the pump cavity, wherein the front cover plate has a cover plate channel connecting the liquid inlet end and the liquid inlet side of the impeller, the front cover plate and the impeller are axially facing each other, and the front cover plate can slide relative to the pump body in the axial direction.

[0005] In some embodiments, the impeller approaches the front cover plate axially but does not contact it during operation.

[0006] In some embodiments, the inlet end has an inlet channel, and the channel wall of the inlet channel is provided with a limiting shoulder, which divides the inlet channel into a small diameter area and a large diameter area, and the large diameter area is distributed closer to the impeller than the small diameter area; The front cover plate includes a first part and a second part connected to each other. The first part is inserted into the large diameter area, and the first part is clearance-fitted with the large diameter area and extends axially. The second part is located in the pump cavity and extends radially. The second part is axially opposite to the impeller.

[0007] In some embodiments, the aperture of the cover plate channel is smaller than the aperture of the liquid inlet channel, and the inner wall of the liquid inlet channel is provided with a variable diameter section, which is located upstream of and adjacent to the limiting shoulder; wherein, the variable diameter section is configured to connect the liquid inlet channel and the cover plate channel.

[0008] In some embodiments, the variable diameter section includes an enlarged diameter section away from the front cover plate and a transition section close to the front cover plate and connected to the enlarged diameter section, wherein the aperture of the enlarged diameter section is larger than the aperture of its upstream region, the aperture of the enlarged diameter section is uniform in size in the liquid inlet direction, and the aperture of the transition section gradually decreases in the liquid inlet direction.

[0009] In some embodiments, the pump chamber wall is provided with a radially extending convex ring, the convex ring is located inside the opening, and the open end of the isolation sleeve abuts against the convex ring. An annular groove is formed between the convex ring and the chamber wall at the opening, and a first sealing ring is provided in the annular groove. The first sealing ring is sandwiched between the convex ring and the open end of the isolation sleeve.

[0010] In some embodiments, the convex ring is part of the flow channel wall of the volute flow channel located on the outer periphery of the impeller. A first gap H1 is predetermined between the outer wall of the impeller assembly located at the convex ring and the annular wall surface extending axially from the convex ring. A second gap H2 is predetermined between the outer wall of the impeller assembly opposite to the opening end of the isolation sleeve and the opening end of the isolation sleeve. A working gap is predetermined between the outer wall of the region of the impeller assembly located inside the isolation sleeve and the cavity wall of the isolation sleeve. A central hole is provided in the center of the impeller assembly, which extends axially through the center and connects the hollow cavity of the isolation sleeve with the cover plate channel. The first gap H1 is connected to the volute flow channel, and the first gap H1, the second gap H2, the working gap, and the central hole are sequentially connected to form a return flow path connecting the volute flow channel and the cover plate channel.

[0011] In some embodiments, the working clearance includes the radial clearance between the circumferential outer wall of the impeller assembly and the circumferential cavity wall of the isolation sleeve, and the axial clearance H3 between the end of the impeller assembly and the end of the isolation sleeve; The radial gap includes a third gap H4 between the outer peripheral wall of the section where the inner magnet is located on the inner magnetic assembly and the circumferential cavity wall of the isolation sleeve, and a fourth gap H5 between the outer peripheral wall of other areas on the inner magnetic assembly besides the section where the inner magnet is located and the circumferential cavity wall of the isolation sleeve. The fourth gap H5 connects the third gap H4 and the second gap H2, and the fourth gap H5 is larger than the third gap H4.

[0012] In some embodiments, the second gap H2 has a gradually decreasing flow cross-section along the fluid flow path, and the end of the central hole away from the impeller is a stepped variable diameter flow channel, which has a decreasing flow cross-section along the impeller assembly to the pump body.

[0013] In some embodiments, a transition plate is provided at one end of the bracket away from the pump body, and the bracket is connected to the motor through the transition plate. The output shaft of the motor extends through the transition plate into the bracket to drive the external magnetic assembly inside the bracket. The external magnetic assembly includes an external magnetic frame and an external magnet disposed on the external magnetic frame. A radially penetrating mounting hole is provided on the circumferential wall of the area on the external magnetic frame that is connected to the output shaft of the motor. A fastener that abuts against the output shaft of the motor is provided in the mounting hole. The transition plate is provided with a radial groove in the same radial direction as the mounting hole, and the radial groove is configured to form an operating channel for external tools to act on the fastener.

[0014] The technical solution provided in this application has the following advantages: In this application, the impeller and the inner magnetic assembly are fixedly connected as a whole to form an impeller assembly. The impeller assembly is suspended in the isolation sleeve by the magnetic coupling between the outer magnet and the inner magnet, which completely eliminates the mechanical rotating components such as the shaft and bearing in the pump body, greatly simplifies the structural design, significantly reduces the axial and radial dimensions of the pump body, and reduces the difficulty of installation and integration. This application sets a relatively small third gap H4 corresponding to the inner magnet region. On the one hand, this shortens the air gap distance between the inner magnetic component and the isolation sleeve, reducing magnetic flux loss during magnetic field transmission and effectively improving magnetic coupling transmission efficiency. On the other hand, it reduces the radial movement margin, and through the fluid medium inside the working gap, it forms fluid damping, radially constraining the inner magnetic component and impeller without shaft support, suppressing eccentric swaying of the impeller and inner magnetic component as a whole, and ensuring stable operation of the impeller assembly. Simultaneously, a larger fourth gap H5 is set in the non-magnetic region of the inner magnetic component. The fourth gap H5 does not adversely affect the magnetic coupling effect and can also increase the flow space of the fluid medium, increase the circulation flow rate of the fluid medium, fully remove heat from the isolation sleeve, and improve heat dissipation conditions. In this application, by differentiating the third gap H4 and the fourth gap H5, magnetic transmission efficiency, impeller assembly operating stability, and the heat dissipation performance of the isolation sleeve can be balanced. The flow cross-section of the second gap H2 gradually narrows, initially accelerating the lower-temperature fluid smoothly, reducing boundary layer separation and vortex generation, and lowering hydraulic losses. The stepped variable-diameter flow channel further increases the fluid velocity, increases the pressure difference between the volute flow channel and the cover plate channel, and increases the driving force for fluid circulation. Through the continuous flow guidance of the second gap H2 and the stepped variable-diameter flow channel, the fluid circulation flow rate through the third gap H4 and the fourth gap H5 is further increased, quickly removing heat from the isolation sleeve. Furthermore, the uniform and stable fluid flowing through the working gap can form continuous and reliable fluid damping, further improving the operational stability of the impeller assembly. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in the specific embodiments of this application or the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0016] Figure 1 A three-dimensional structural diagram of the high-speed pump provided in this application; Figure 2 A cross-sectional structural schematic diagram of the high-speed pump provided in this application; Figure 3 An exploded view of part of the structure of the high-speed pump provided in this application; Figure 4 This is an exploded structural diagram of the high-speed pump provided in this application; Figure 5 This is a schematic diagram of the three-dimensional structure of the pump body; Figure 6 This is a schematic cross-sectional view of the pump body. Figure 7 This is a schematic diagram of the three-dimensional structure of the support. Figure 8 This is a three-dimensional structural diagram of the isolation sleeve; Figure 9 This is a three-dimensional structural diagram of the impeller assembly; Figure 10 for Figure 2 Enlarged structural diagram of region A in the middle; Figure 11 for Figure 2 A magnified structural diagram of region B in the middle; Figure 12 for Figure 2 A magnified structural diagram of region C in the middle; Figure 13 This is a schematic diagram of the three-dimensional structure of the transition disk; Figure 14This is a schematic diagram of the external magnetic assembly from a first-view perspective. Figure 15 This is a schematic diagram of the external magnetic assembly from a second perspective. Detailed Implementation

[0017] The technical solutions of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. This application will be described in detail below with reference to the accompanying drawings and embodiments. It should be noted that, unless otherwise specified, the embodiments and features in the embodiments of this application can be combined with each other.

[0018] It should be noted that the terms "first," "second," etc., in the specification, claims, and drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence.

[0019] In this application, unless otherwise stated, directional terms such as "upper," "lower," "top," and "bottom" are generally used in relation to the direction shown in the accompanying drawings, or in relation to the vertical, perpendicular, or gravitational direction of the component itself; similarly, for ease of understanding and description, "inner" and "outer" refer to the inner and outer contours of each component itself, but the above directional terms are not intended to limit this application.

[0020] This application provides a high-speed pump. The high-speed pump uses a high-speed rotating impeller to do work on the liquid, so that the liquid gains high-speed kinetic energy. The high-speed liquid decelerates and diffuses in the pump, converting kinetic energy into liquid pressure, thereby realizing high-pressure delivery and pumping of liquid.

[0021] like Figures 1 to 4 As shown, the high-speed pump includes at least a pump body 100, a bracket 200, an isolation sleeve 300, an impeller assembly 400, an external magnetic assembly 500, and a front cover plate 600. The pump body 100 has a pump chamber 110 formed inside, with an opening at the first end of the pump body 100. The bracket 200 is located at the first end of the pump body 100. The isolation sleeve 300 is also located at the first end and is sandwiched between the pump body 100 and the bracket 200.

[0022] In this application, the isolation sleeve 300 abuts against the pump body 100, and the isolation sleeve 300 also abuts against the support 200. There is no connecting structure between the isolation sleeve 300 and the pump body 100, nor between the isolation sleeve 300 and the support 200. The impeller assembly 400 is housed within the space formed by the pump body 100 and the isolation sleeve 300. It is worth noting that the terms "axial" and "radial" and "circumferential" mentioned below are all based on the axial, radial, and circumferential directions of the impeller assembly 400.

[0023] like Figure 5, Figure 6 and Figure 11 As shown, a radially extending convex ring 113 is provided on the cavity wall of the pump chamber 110. The convex ring 113 is located inside the opening of the pump body 100, and the open end of the isolation sleeve 300 abuts against the convex ring 113. An annular groove is formed between the convex ring 113 and the cavity wall at the opening. To ensure a sealing effect, a first sealing ring 700 is provided in the annular groove. The first sealing ring 700 is sandwiched between the convex ring 113 and the open end of the isolation sleeve 300. Through the above structure, the isolation sleeve 300 can be clearly positioned in the axial direction, and the first sealing ring 700 is located at the clamping interface to form a sealing boundary at the open end of the isolation sleeve 300. The first sealing ring 700 can be an elastic sealing gasket, a flat gasket, or other annular gasket suitable for clamping and sealing; the specific material is not limited.

[0024] Furthermore, such as Figure 2 , Figure 8 and Figure 11 As shown, the opening end of the isolation sleeve 300 is turned outward to form a limiting flange 310, which abuts against the pump body 100 and the bracket 200. One side of the limiting flange 310 abuts against the protruding ring 113 on the pump body 100, and the opposite side of the limiting flange 310 abuts against the bracket 200. The limiting flange 310 is partially located within the annular groove and partially extends to the outside of the annular groove. The first sealing ring 700 abuts against the protruding ring 113 and the limiting flange 310.

[0025] like Figures 5 to 7 As shown, the isolation sleeve 300 is partially located inside the bracket 200 and partially extends to the outside of the bracket 200. The bracket 200 includes a barrel-shaped circumferential wall portion 210, a first mounting wall portion 220 and a second mounting wall portion 230 located at both axial ends of the circumferential wall portion 210. The bracket 200 is connected to the pump body 100. In one embodiment, the first mounting wall portion 220 is provided with a first connecting hole 223, and the pump body 100 is provided with a second connecting hole 114 that mates with the first connecting hole 223. The pump body 100 and the bracket 200 are connected by bolts.

[0026] A clearance opening 221 is provided in the center of the first mounting wall portion 220, and the isolation sleeve 300 passes through the clearance opening 221. The limiting flange 310 is located on the outside of the bracket 200 and abuts against the first mounting wall portion 220 in the axial direction. That is, the limiting flange 310 abuts between the convex ring 113 of the pump body 100 and the first mounting wall portion 220 of the bracket 200. The convex ring 113 and the first mounting wall portion 220 of the bracket 200 will apply an axial clamping force to the limiting flange 310 from both axial sides, so that the position of the isolation sleeve 300 will not move. The outer diameter of the limiting flange 310 is larger than the outer diameter of the body of the isolation sleeve 300, and the outer diameter of the body of the isolation sleeve 300 is equal to the diameter of the clearance opening 221.

[0027] In one embodiment, the first mounting wall portion 220 has a recessed limiting groove 222 on its end face near the pump body 100, which mates with the limiting flange 310 of the isolation sleeve 300. The limiting groove 222 is coaxially distributed with the clearance opening 221. In one embodiment, the limiting flange 310 is embedded inside the limiting groove 222. Compared with the method of only end face contact, the limiting groove 222 can achieve both radial constraint and axial abutment of the limiting flange 310, preventing radial displacement of the isolation sleeve 300 during assembly and effectively ensuring the installation accuracy of the isolation sleeve 300.

[0028] In another embodiment, such as Figure 7 and Figure 11 As shown, a limiting groove 222 is recessed on the end face of the first mounting wall portion 220 near the pump body 100. A second sealing ring 710 is provided in the limiting groove 222, and a limiting flange 310 abuts against the second sealing ring 710. The limiting flange 310 may be partially located inside the limiting groove 222 or outside the limiting groove 222.

[0029] like Figure 11 As shown, there is an axial gap M between the pump body 100 and the bracket 200. The pump body 100, bracket 200, and isolation sleeve 300 all have dimensional deviations during manufacturing. If there were no axial gap M between the pump body 100 and the bracket 200, when the part size is too large, the isolation sleeve 300 would be forcibly squeezed during assembly, causing deformation or even cracking. Furthermore, the aforementioned gap M provides a stable preload, preventing the isolation sleeve 300 from loosening under vibration conditions, and simultaneously improving the sealing effect of the isolation sleeve 300.

[0030] like Figure 1 As shown, the pump body 100 is also provided with an inlet end 120 and an outlet end 130 communicating with the pump chamber 110. The inlet end 120 and the outlet end 130 are respectively connected to an external flow path (not shown in the figure). The inlet end 120 is used for liquid inlet, and the outlet end 130 is used for liquid outlet. The inlet end 120 is distributed axially, and the outlet end 130 is distributed tangentially in the circumferential direction. The inlet end 120 is coaxially distributed with the impeller assembly 400.

[0031] like Figure 2 and Figure 9As shown, the impeller assembly 400 is disposed within the space enclosed by the pump body 100 and the isolation sleeve 300. The impeller assembly 400 includes an impeller 410 and an inner magnetic assembly 420 connected to the impeller 410. The inner magnetic assembly 420 and the impeller 410 are connected to form a whole. When the inner magnetic assembly 420 rotates, it can drive the impeller 410 to rotate synchronously. It is worth noting that the impeller assembly 400 can be formed by the impeller 410 and the inner magnetic assembly 420 fixedly connected, or it can be a one-piece molded structure, or it can adopt other forms of assembly connection, as long as it can rotate synchronously during operation.

[0032] Compared to the traditional method of transmission relying on a rotating shaft and bearings, this application integrates the internal magnetic assembly 420 and the impeller 410 into a single unit, eliminating the need for mechanical rotating components such as the rotating shaft and bearings, and also eliminating the need for a separate circumferential limiting structure between the impeller and the rotating shaft. This offers the following advantages: fewer parts, a simpler internal layout, reduced overall space occupation, and facilitates miniaturization; in the traditional structure, torque passes sequentially through the internal magnet, rotating shaft, and impeller, resulting in frictional losses during shaft and bearing rotation. In this application, the internal magnetic assembly 420 directly drives the impeller 410, eliminating intermediate transmission links, avoiding bearing friction energy loss, and the magnetic driving force acts directly on the impeller 410, significantly improving transmission efficiency; in the traditional structure, high-speed frictional heat generation of the bearings necessitates the creation of cooling channels inside the rotating shaft to cool the bearings. This application eliminates the rotating shaft and bearings, eliminating bearing heat generation issues and the need for cooling channels. This saves on deep hole machining of the rotating shaft, reducing processing costs, and avoids hydraulic losses and rotating shaft cracking caused by cooling channels, optimizing the flow state of the medium inside the pump and improving the overall working efficiency of the pump.

[0033] like Figure 2 and Figure 14 As shown, the outer magnetic assembly 500 is disposed within the bracket 200 and located on the outer periphery of the isolation sleeve 300. The outer magnet 520 on the outer magnetic assembly 500 and the inner magnet (not shown) on the inner magnetic assembly 420 overlap at least partially in the axial direction to form a magnetic coupling transmission, thereby driving the impeller 410 to rotate. Specifically, the magnetic coupling overlap area between the outer magnetic assembly 500 and the inner magnetic assembly 420 can be set to partially or fully overlap in the axial direction according to the torque transmission requirements.

[0034] like Figures 2 to 4 The front cover plate 600 is mounted on the pump body 100 and located within the pump chamber 110. The front cover plate 600 has a cover plate channel 601 that connects the liquid inlet end 120 to the liquid inlet side of the impeller 410. The front cover plate 600 and the impeller 410 are axially facing each other, and the front cover plate 600 can slide relative to the pump body 100 axially. There is no rigid contact between the impeller 410 and the front cover plate 600. During operation, the impeller 410 approaches the front cover plate 600 axially but does not come into contact with it.

[0035] It is worth noting that the axial movement of the front cover plate 600 relative to the pump body 100 is a result of the operation state, and the axial clearance between the front cover plate 600 and the impeller 410 can be adjusted accordingly depending on the operation state. This axial sliding can be passively achieved by fluid pressure difference and fluid action, and is not limited to setting up a separate active drive adjustment mechanism.

[0036] During operation, the front cover plate 600 forms a small working gap towards the impeller 410 to compress the crossflow space near the liquid inlet side of the impeller 410, while also preventing mechanical friction or contact interference between the two. This maintains stability during high-speed operation and also helps reduce fluid leakage caused by excessive axial clearance.

[0037] In this application, as Figure 2 and Figure 6 As shown, the inlet end 120 has an inlet channel 121, which communicates with the pump chamber 110. A limiting shoulder 111 is provided on the channel wall of the inlet channel 121, dividing the inlet channel 121 axially into a small-diameter region and a large-diameter region. The large-diameter region is closer to the impeller 410 than the small-diameter region. The axial dimension of the large-diameter region is smaller than that of the small-diameter region.

[0038] like Figure 4 As shown, the front cover plate 600 includes a first part 610 and a second part 620 connected to each other. The first part 610 is inserted into the large-diameter area, and the second part 620 is located outside the large-diameter area. The first part 610 has a clearance fit with the large-diameter area and extends axially. When the first part 610 moves axially within the large-diameter area, it can provide guidance, centering, and limiting functions. During axial sliding, the front cover plate 600 can ensure the coaxiality between the liquid inlet channel 121 and the cover plate channel 601.

[0039] The second part 620 is located within the pump chamber 110 and extends radially, with the second part 620 axially facing the impeller 410. The first part 610 is a hollow tube, and the second part 620 can be a disc-shaped, annular, or other radially expanding cover plate structure, as long as it is located within the pump chamber 110 and arranged facing the impeller 410. The second part 620 can form a cover plate body near the liquid inlet side of the impeller 410.

[0040] In this application, the aperture of the cover channel 601 is smaller than the aperture of the liquid inlet channel 121. For example... Figure 6 As shown, a variable diameter section 112 is provided on the inner wall of the liquid inlet channel 121. The variable diameter section 112 is located upstream of and adjacent to the limiting hole shoulder 111. The variable diameter section 112 is configured to connect the liquid inlet channel 121 and the cover plate channel 601.

[0041] When the fluid medium enters from the inlet end 120, it first flows axially along the inlet channel 121, and enters the variable diameter section 112 before approaching the front cover plate 600. The flow channel cross-section is adjusted through the variable diameter section 112, and then it enters the cover plate channel 601, finally reaching the inlet side of the impeller 410. In this way, the inlet channel 121 and the cover plate channel 601 form an orderly transition through the variable diameter section 112.

[0042] Specifically, such as Figure 6 As shown, the variable diameter section 112 includes an enlarged diameter section 1121 on the side away from the front cover plate 600 and a transition section 1122 on the side close to the front cover plate 600 and connected to the enlarged diameter section 1121. The aperture of the enlarged diameter section 1121 is larger than the aperture of its upstream region, and the aperture of the enlarged diameter section 1121 is uniform in the liquid inlet direction. The aperture of the transition section 1122 gradually decreases in the liquid inlet direction. The transition between the enlarged diameter section 1121 and the transition section 1122 can be achieved using a curved surface transition, a stepped transition, or a smooth contour transition, as long as the segmented relationship between the enlarged diameter section 1121 and the transition section 1122 is maintained.

[0043] The orifice diameter of the expansion section 1121 is larger than that of the upstream channel. After the fluid medium enters the expansion section 1121, the flow velocity decreases, and fluid turbulence is alleviated. This helps reduce eddies and bubbles, stabilizes fluid pressure, and improves inlet conditions. The orifice diameter of the transition section 1122 gradually decreases along the inlet direction, allowing the fluid to accelerate smoothly. Unlike a step-like abrupt contraction, the gradually narrowing structure reduces fluid boundary layer separation, lowers local hydraulic losses, improves hydraulic efficiency, and allows the medium velocity to increase steadily, resulting in a uniform velocity distribution of the medium entering the impeller 410. Furthermore, the gradually narrowing transition section 1122 eliminates vortices caused by the right-angle step formed between the expansion section 1121 and its upstream section, suppressing turbulence, reducing fluid impact noise, and lowering operating noise. The right-angle step formed between the expansion section 1121 and its upstream section ensures a smooth wall thickness transition, preventing local wall thinning caused by rounded inner corners. The wall thickness at the right-angle step maintains a certain thickness, resulting in better structural rigidity and the ability to withstand fluid pressure, thus exhibiting good pressure resistance.

[0044] Within the expansion section 1121, the fluid velocity slows down and the static pressure increases, raising the static pressure value of the fluid medium. This reduces the probability of negative pressure generating bubbles, alleviating cavitation problems and preventing bubble bursts from impacting the impeller 410 surface, thus preventing erosion damage to the impeller 410. After converging in the transition section 1122, the fluid medium converges towards the center of the inlet channel 121. The fluid medium enters the impeller 410 more concentratedly through the cover channel 601 of the front cover plate 600, reducing fluid medium adhesion to the channel wall. This results in a more uniform distribution of the inlet flow to each blade on the impeller 410, improving the internal flow field distribution and effectively enhancing overall working efficiency.

[0045] like Figure 2 , Figure 6 , Figure 11 As shown, the convex ring 113 is part of the flow channel wall of the volute flow channel 115 located on the outer periphery of the impeller 410. The volute flow channel 115 is located inside the pump body 100 and can be regarded as part of the pump cavity 110. The convex ring 113 not only participates in the installation and positioning of the isolation sleeve 300, but also participates in the formation of the fluid boundary within the pump cavity 110. A first gap H1 is preset between the outer wall of the impeller assembly 400 located at the convex ring 113 and the annular wall surface extending axially from the convex ring 113. A second gap H2 is preset between the outer wall of the impeller assembly 400 opposite to the open end of the isolation sleeve 300 and the open end of the isolation sleeve 300. A working gap is preset between the outer wall of the section of the impeller assembly 400 located within the isolation sleeve 300 and the cavity wall of the isolation sleeve 300. A central hole 430 is provided in the center of the impeller assembly 400, which extends axially through it. The central hole 430 connects the hollow cavity of the isolation sleeve 300 and the cover plate channel 601.

[0046] The first gap H1 is connected to the volute flow channel 115. The first gap H1, the second gap H2, the working gap, and the central hole 430 are sequentially connected to form a return flow path connecting the volute flow channel 115 and the cover plate channel 601. Thus, the fluid medium in the pump chamber 110 can enter the second gap H2 through the first gap H1, then enter the working gap, and further flow into the central hole 430, finally connecting with the cover plate channel 601, thereby forming a return flow path.

[0047] When the inner magnetic component 420 and the outer magnetic component 500 are magnetically coupled, a large amount of heat will be generated in the isolation sleeve 300. The fluid medium flowing through the above-mentioned return path can carry away the heat generated in the isolation sleeve 300 and transport it to the pump body 100, thereby effectively realizing the heat dissipation of the isolation sleeve 300 and avoiding overheating inside the isolation sleeve 300.

[0048] In this application, the aforementioned return flow path is formed by interconnecting the gaps created after the assembly of each component. Compared with the prior art, which uses additional dedicated through holes machined on the component body to arrange cooling channels, this application eliminates the need for separate hole machining, resulting in a simpler component body structure, fewer machining steps, and lower manufacturing costs.

[0049] The flow cross-section of the second gap H2 gradually decreases along the fluid flow path, and the end of the central hole 430 away from the impeller 410 is a stepped variable diameter flow channel 431. The flow cross-section of the stepped variable diameter flow channel 431 decreases along the direction from the impeller assembly 400 to the pump body 100.

[0050] The second gap H2, located at the front of the return flow path, has a gradually narrowing guiding characteristic. The stepped variable diameter flow channel 431, located at the rear of the return flow path, further guides the fluid, resulting in good flow guidance. The aforementioned stepped variable diameter flow channel 431 can be formed by two steps or multiple steps, but all maintain the characteristic of decreasing flow cross-section in the direction of the pump body 100.

[0051] The aforementioned work intervals can be further subdivided into different areas, as shown in the figure. Figure 11 and Figure 12 As shown, the working clearance includes the radial clearance between the circumferential outer wall of the impeller assembly 400 and the circumferential cavity wall of the isolation sleeve 300, and the axial clearance H3 between the end of the impeller assembly 400 and the end of the isolation sleeve 300.

[0052] The radial gaps include a third gap H4 between the outer peripheral wall of the section containing the inner magnet on the inner magnetic assembly 420 and the circumferential cavity wall of the isolation sleeve 300, and a fourth gap H5 between the outer peripheral walls of other areas on the inner magnetic assembly 420 besides the section containing the inner magnet and the circumferential cavity wall of the isolation sleeve 300. The fourth gap H5 connects the third gap H4 and the second gap H2, and the fourth gap H5 is larger than the third gap H4. As can be seen from the above, the working gap is not a single uniform space, but a partitioned, interconnected space composed of gaps of different sizes and positions.

[0053] This application sets the third gap H4 corresponding to the inner magnet region to be relatively small. On the one hand, this shortens the air gap distance between the inner magnetic component 420 and the isolation sleeve 300, reducing magnetic flux loss during magnetic field transmission and effectively improving magnetic coupling transmission efficiency. On the other hand, it reduces the radial movement margin, and through the fluid medium inside the working gap, it forms fluid damping, radially constraining the inner magnetic component 420 and impeller 410 without shaft support, suppressing eccentric swaying of the impeller 410 and the inner magnetic component 420 as a whole, and ensuring the smooth operation of the impeller assembly 400. At the same time, a larger fourth gap H5 is set in the non-magnetic region of the inner magnetic component 420. The fourth gap H5 does not adversely affect the magnetic coupling effect, and can also increase the flow space of the fluid medium, increase the circulation flow rate of the fluid medium, and fully remove the heat inside the isolation sleeve 300, improving heat dissipation conditions. In this application, by differentiating the third gap H4 and the fourth gap H5, the magnetic transmission efficiency, the operational stability of the impeller assembly 400, and the heat dissipation performance of the isolation sleeve 300 can be balanced.

[0054] The flow cross-section of the second gap H2 gradually narrows, initially accelerating the lower-temperature fluid smoothly, reducing boundary layer separation and vortex generation, and lowering hydraulic losses. The stepped variable-diameter flow channel 431 further increases the fluid velocity, increases the pressure difference between the volute flow channel 115 and the cover plate channel 601, and increases the driving force for fluid circulation. Through the continuous flow guidance of the second gap H2 and the stepped variable-diameter flow channel 431, the fluid circulation flow rate through the third gap H4 and the fourth gap H5 is further increased, quickly removing heat from the isolation sleeve 300. Furthermore, the uniform and stable fluid flowing through the working gap can form continuous and reliable fluid damping, further improving the operational stability of the impeller assembly.

[0055] In this application, a transition plate 800 is provided at the end of the bracket 200 away from the pump body 100, and the bracket 200 is connected to the motor 810 through the transition plate 800. The second mounting wall 230 of the bracket 200 is connected to the transition plate 800. In one embodiment, the motor 810, the transition plate 800, and the second mounting wall 230 of the bracket 200 are connected by long bolts.

[0056] like Figure 2 , Figure 13 , Figure 14 and Figure 15 As shown, the output shaft of motor 810 extends through transition plate 800 into bracket 200 for transmission connection with external magnetic assembly 500 within bracket 200. External magnetic assembly 500 includes external magnetic frame 510 and external magnet 520 disposed on external magnetic frame 510. A radially penetrating mounting hole 511 is provided on the circumferential wall of the area on external magnetic frame 510 where it connects with the output shaft of motor 810. A fastener abuts against the output shaft of motor 810 within the mounting hole 511. During assembly, after the output shaft of motor 810 extends into the connection area of ​​external magnetic frame 510, the fastener can act inward through the mounting hole 511 and abut against the output shaft, thereby locking external magnetic frame 510 onto the output shaft of motor 810. The fastener can be a set screw, bolt, or other fastener suitable for abutting against the output shaft within the mounting hole 511.

[0057] The transition plate 800 has a radial groove 801 located in the same radial direction as the mounting hole 511. The radial groove 801 is configured to form an operating channel for external tools to act on the fastener. External tools can approach the fastener in the mounting hole 511 radially via the radial groove 801 on the transition plate 800 to perform tightening, loosening, or adjustment operations on the fastener. The radial groove 801 can be a through groove, an open groove, or other clearance channel for the insertion of external tools, as long as it is in the same radial direction as the mounting hole 511 and allows the tool to act on the fastener.

[0058] Obviously, the embodiments described above are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, those skilled in the art can make other variations or modifications without creative effort, and all such variations or modifications should fall within the scope of protection of this application.

Claims

1. A high-speed pump, characterized in that, include: The pump body (100) has a pump chamber (110) inside. The pump chamber (110) has an opening at the first end of the pump body (100). The pump body (100) is also provided with an inlet end (120) and an outlet end (130) that communicate with the pump chamber (110). A bracket (200) is provided at the first end of the pump body (100); An isolation sleeve (300) is provided at the first end and located inside the bracket (200), and sandwiched between the pump body (100) and the bracket (200); An impeller assembly (400) is disposed within the space enclosed by the pump body (100) and the isolation sleeve (300). The impeller assembly (400) includes an impeller (410) and an internal magnetic assembly (420) connected to the impeller (410). An external magnetic assembly (500) is disposed inside the bracket (200) and located on the outer periphery of the isolation sleeve (300). The external magnet (520) on the external magnetic assembly (500) and the internal magnet on the internal magnetic assembly (420) overlap at least partially in the axial direction to form a magnetic coupling transmission to drive the impeller (410) to rotate. A front cover plate (600) is provided on the pump body (100) and located in the pump chamber (110). The front cover plate (600) is provided with a cover plate channel (601) that connects the liquid inlet end (120) and the liquid inlet side of the impeller (410). The front cover plate (600) and the impeller (410) are arranged facing each other in the axial direction, and the front cover plate (600) can slide relative to the pump body (100) in the axial direction.

2. The high-speed pump as described in claim 1, characterized in that, During operation, the impeller (410) approaches the front cover plate (600) axially but does not come into contact with it.

3. The high-speed pump as described in claim 1, characterized in that, The liquid inlet end (120) has a liquid inlet channel (121), and the channel wall of the liquid inlet channel (121) is provided with a limiting shoulder (111). The limiting shoulder (111) divides the liquid inlet channel (121) into a small diameter area and a large diameter area. The large diameter area is closer to the impeller (410) than the small diameter area. The front cover plate (600) includes a first part (610) and a second part (620) connected to each other. The first part (610) is inserted into the large diameter area. The first part (610) is clearance-fitted with the large diameter area and extends axially. The second part (620) is located in the pump chamber (110) and extends radially. The second part (620) and the impeller (410) are axially opposite to each other.

4. The high-speed pump as described in claim 3, characterized in that, The aperture of the cover plate channel (601) is smaller than the aperture of the liquid inlet channel (121). The inner wall of the liquid inlet channel (121) is provided with a variable diameter section (112). The variable diameter section (112) is located upstream of the limiting hole shoulder (111) and is distributed adjacent to it. The variable diameter section (112) is configured to connect the liquid inlet channel (121) and the cover plate channel (601).

5. The high-speed pump as described in claim 4, characterized in that, The variable diameter section (112) includes an enlarged diameter section (1121) away from the front cover plate (600) and a transition section (1122) close to the front cover plate (600) and connected to the enlarged diameter section (1121). The diameter of the enlarged diameter section (1121) is larger than the diameter of its upstream region. The diameter of the enlarged diameter section (1121) is consistent in size in the liquid inlet direction. The diameter of the transition section (1122) gradually decreases in size in the liquid inlet direction.

6. The high-speed pump as described in claim 1, characterized in that, The pump chamber (110) has a radially extending protruding ring (113) on its cavity wall. The protruding ring (113) is located inside the opening. The opening end of the isolation sleeve (300) abuts against the protruding ring (113). An annular groove is formed between the protruding ring (113) and the cavity wall at the opening. A first sealing ring (700) is provided in the annular groove. The first sealing ring (700) is sandwiched between the protruding ring (113) and the opening end of the isolation sleeve (300).

7. The high-speed pump as described in claim 1, characterized in that, The convex ring (113) is part of the flow channel wall of the volute flow channel (115) located on the outer periphery of the impeller (410). A first gap H1 is preset between the outer wall of the impeller assembly (400) located at the convex ring (113) and the annular wall surface extending axially from the convex ring (113). A second gap H2 is preset between the outer wall of the impeller assembly (400) opposite to the opening end of the isolation sleeve (300) and the opening end of the isolation sleeve (300). A working gap is preset between the outer wall of the region of the impeller assembly (400) located inside the isolation sleeve (300) and the cavity wall of the isolation sleeve (300). A central hole (430) is provided in the center of the impeller assembly (400) and extends axially through it. The central hole (430) connects the hollow cavity of the isolation sleeve (300) and the cover plate channel (601). The first gap H1 is connected to the volute flow channel (115), and the first gap H1, the second gap H2, the working gap, and the center hole (430) are connected in sequence to form a return flow path connecting the volute flow channel (115) and the cover plate channel (601).

8. The high-speed pump as described in claim 7, characterized in that, The working clearance includes the radial clearance between the circumferential outer wall of the impeller assembly (400) and the circumferential cavity wall of the isolation sleeve (300), and the axial clearance H3 between the end of the impeller assembly (400) and the end of the isolation sleeve (300); The radial gaps include a third gap H4 between the outer peripheral wall of the section where the inner magnet is located on the inner magnetic assembly (420) and the circumferential cavity wall of the isolation sleeve (300), and a fourth gap H5 between the outer peripheral wall of other areas on the inner magnetic assembly (420) other than the section where the inner magnet is located and the circumferential cavity wall of the isolation sleeve (300). The fourth gap H5 connects the third gap H4 and the second gap H2, and the fourth gap H5 is greater than the third gap H4.

9. The high-speed pump as described in claim 7, characterized in that, The second gap H2 has a gradually decreasing cross-section along the flow path of the fluid. The end of the central hole (430) away from the impeller (410) is a stepped variable diameter flow channel (431). The stepped variable diameter flow channel (431) has a decreasing cross-section along the impeller assembly (400) to the pump body (100).

10. The high-speed pump as described in claim 1, characterized in that, The bracket (200) has a transition plate (800) at one end away from the pump body (100). The bracket (200) is connected to the motor (810) through the transition plate (800). The output shaft of the motor (810) extends through the transition plate (800) into the bracket (200) to drive the external magnetic assembly (500) inside the bracket (200). The external magnetic assembly (500) includes an external magnetic frame (510) and an external magnet (520) disposed on the external magnetic frame (510). A radially penetrating mounting hole (511) is provided on the circumferential wall of the area on the external magnetic frame (510) that is connected to the output shaft of the motor (810). A fastener that abuts against the output shaft of the motor (810) is provided in the mounting hole (511). The transition plate (800) is provided with a radial groove (801) located in the same radial direction as the mounting hole (511), and the radial groove (801) is configured to form an operating channel for external tools to act on the fastener.

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