Opposite-rotating flow channel rotating wheel magnetic drive pump

Abstract

The invention provides a counter-rotating runner rotating wheel magnetic drive pump which comprises a shell, a front rotating wheel and a rear rotating wheel, the front rotating wheel is supported on the front portion of the shell, and the front rotating wheel is driven by a front magnetic drive device to rotate; the rear rotating wheel is supported on the rear portion of the shell, and the rear rotating wheel is driven by the rear magnetic driving device to rotate reversely relative to the front rotating wheel. Spiral runners are respectively arranged on the runner surfaces of the front rotating wheel and the rear rotating wheel, and one end of the rear rotating wheel is nested in the runner of the front rotating wheel, so that long fibers and high-viscosity mixed fluid can be effectively conveyed; one end of the cross section of the spiral flow channel is provided with an outwards-extending protruding end, and when fibers are wound around the impeller, the outwards-extending protruding ends of the front rotating wheel and the rear rotating wheel can cut off the fibers, so that the fibers can be effectively prevented from being wound around the impeller, and the flow channel is prevented from being blocked.

Description

Technical Field

[0001] The invention relates to the field of liquid pumps, and in particular to a counter-rotating flow channel rotor magnetic pump. Background Art

[0002] As an important mechanical equipment, it has been widely used in various fields of national production. The energy transmission structure of a conventional pump is usually composed of a rotating impeller and one or more blades on the impeller. The high-speed rotating blades provide kinetic energy for the medium. When conveying a mixed flow containing long fibers, it is very easy to get entangled on the impeller or shaft. Therefore, in order to solve the above problem, a counter-rotating flow channel rotor magnetic pump is needed.

[0003] The prior art has disclosed a fiber pump for conveying fiber materials. The fiber pump provided by the invention adopts longer swirl blades and removes the front and rear cover plates, which can prevent the fiber materials from being entangled on the blades. However, the longer fiber materials may still be entangled on the shaft of the impeller or be cut off by the high-speed rotating blades. Therefore, it is only suitable for conveying shorter fiber mixtures; a Chinese patent has also disclosed a spiral pump. The spiral pump provided by the invention is mainly capable of removing dirt on the surface of the blades. The Chinese patent has also disclosed a hydraulic optimization method for an efficient and wear-resistant solid-liquid two-phase mixed pump. The two-phase mixed pump provided by the invention can convey particulate solids, but is not suitable for conveying soft solids or mixed fluids of long fibers.

[0004] The existing technology cannot solve the problem of stable transportation of long fibers or slightly larger soft solid mixtures under high-speed rotation of the impeller. When a conventional impeller processes a fiber-containing fluid, the fibers will be disturbed by the impeller blades and are very likely to be entangled or cut off. Alternatively, a peristaltic pump with a rubber structure is used, but the peristaltic pump has a small flow rate and a short life. Therefore, a counter-rotating flow channel rotor magnetic pump is needed that can achieve large-scale mixed transportation of long fibers or mixed fluids containing slightly larger soft solids. Summary of the invention

[0005] In view of the shortcomings of the prior art, the present invention provides a counter-rotating flow channel rotor magnetic pump, in which the front wheel and the rear wheel rotate in opposite directions, and the flow channel surfaces of the front wheel and the rear wheel are respectively provided with spiral flow channels, and one end of the rear wheel is nested in the flow channel of the front wheel to ensure that long fibers or high-viscosity fluids can pass smoothly.

[0006] The present invention achieves the above technical objectives through the following technical means.

[0007] A counter-rotating flow channel rotor magnetic pump comprises a shell, a front rotor and a rear rotor, wherein the front rotor is supported at the front of the shell and driven to rotate by a front magnetic drive device; the rear rotor is supported at the rear of the shell and driven to rotate in the opposite direction relative to the front rotor by a rear magnetic drive device; spiral flow channels are respectively provided on the flow channel surfaces of the front rotor and the rear rotor, and one end of the rear rotor is nested in the flow channel of the front rotor for multi-stage speed increase.

[0008] Furthermore, the flow channel in the front impeller includes a W-shaped flow channel and an inlet flow channel that are interconnected, the inlet flow channel is connected to the shell inlet, the inlet flow channel is located at the center of the W-shaped flow channel, and a front spiral groove type flow channel structure is provided on the flow channel surface of the front impeller; the rear impeller is in a cone shape, and a central flow channel is provided at the center of the rear impeller, the central flow channel is nested in the W-shaped flow channel, and the inlet flow channel is nested in the central flow channel for diverting the central flow channel; a rear spiral groove type flow channel structure is provided on the contour of the cone-shaped rear impeller.

[0009] Furthermore, the front spiral groove type flow channel structure includes a first-level groove type flow channel, a third-level groove type flow channel and a fourth-level groove type flow channel. The inner wall of the inlet flow channel is provided with a first-level groove type flow channel, and the W-shaped flow channel is respectively provided with a third-level groove type flow channel and a fourth-level groove type flow channel, and the third-level groove type flow channel is located on the outer side of the inlet flow channel wall; the first-level groove type flow channel and the third-level groove type flow channel are horizontal spiral flow channels, and the fourth-level groove type flow channel is a spiral flow channel that gradually expands along the flow direction.

[0010] Furthermore, the gradually expanding spiral flow channel angle α of the fourth-stage groove flow channel is 1 The value range is 20°~50°.

[0011] Furthermore, the rear spiral groove type flow channel structure includes a second-level groove type flow channel and a fifth-level groove type flow channel. The inner wall surface of the central flow channel is provided with a second-level groove type flow channel, and the outer side of the contour of the rear impeller is provided with a fifth-level groove type flow channel. The second-level groove type flow channel and the fifth-level groove type flow channel are both spiral flow channels that gradually expand along the flow direction.

[0012] Furthermore, the gradually expanding spiral flow channel angle α of the second-stage groove flow channel is 2 The value range is 10°~30°; the outer contour of the rear wheel is arc-shaped, and the radius R of the arc-shaped outer contour is 1 It is 0.4 to 1.0 times the maximum diameter Φ of the rear runner.

[0013] Furthermore, the length L of the rear wheel support at the rear of the housing is 2 0.75 to 1.0 times the center flow channel length L 1 .

[0014] Furthermore, one end of the cross section of the spiral flow channel is provided with an outwardly extending protruding end for cutting fibers.

[0015] Furthermore, a front permanent magnet is embedded in the front wheel, and a front coil group is arranged on the side wall of the shell corresponding to the front permanent magnet, and the front wheel is rotated by generating a magnetic field by the front coil group; a rear permanent magnet is embedded in the rear wheel, and a rear coil group is arranged on the side wall of the shell corresponding to the rear permanent magnet, and the rear wheel is rotated by generating a magnetic field by the rear coil group; the rotational speed of the front wheel and the rear wheel is 600-1450rpm.

[0016] Furthermore, the front rotating wheel is supported at the front of the shell through a front sliding sleeve, and a front spiral cooling channel is arranged on the inner side of the front sliding sleeve; the rear rotating wheel is supported at the rear of the shell through a rear sliding sleeve, and a rear spiral cooling channel is arranged on the inner side of the rear sliding sleeve.

[0017] The beneficial effects of the present invention are:

[0018] 1. The counter-rotating flow channel rotor magnetic pump described in the present invention rotates in opposite directions through the front rotor and the rear rotor, and the flow channel surfaces of the front rotor and the rear rotor are respectively provided with spiral flow channels, and one end of the rear rotor is nested in the flow channel of the front rotor to ensure that long fibers or high-viscosity fluids can pass smoothly.

[0019] 2. The counter-rotating flow channel impeller magnetic pump described in the present invention has spiral flow channels on the flow channel surfaces of the front impeller and the rear impeller, respectively, which can effectively transport long fibers and high-viscosity mixed fluids; one end of the cross section of the spiral flow channel is provided with an outwardly extending protruding end, and when the fibers are wound around the impeller, the outwardly extending protruding ends of the front impeller and the rear impeller can cut them off, which can effectively prevent the fibers from being wound around the impeller and avoid blockage of the flow channel.

[0020] 3. The counter-rotating flow channel rotor magnetic pump described in the present invention, wherein the central flow channel is nested in the W-shaped flow channel, and the inlet flow channel is nested in the central flow channel, can realize multiple pressurization and speed-up of the conveying fluid at low speed.

[0021] 4. The counter-rotating flow channel impeller magnetic pump described in the present invention drives the front impeller and the rear impeller through magnetic force, thus avoiding the need for a rotating drive mechanical structure such as a motor, and reducing operating noise and mechanical maintenance costs.

[0022] 5. The counter-rotating flow channel impeller magnetic pump described in the present invention reduces the friction resistance between the impeller and the pump body through the silicon carbide friction ring and the polytetrafluoroethylene sliding bearing, and cools the friction structure in time through the coolant. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. The drawings described below are some embodiments of the present invention. For ordinary technicians in this field, it is obvious that other drawings can be obtained based on these drawings without paying any creative work.

[0024] Figure 1 This is a schematic diagram of the structure of the counter-rotating flow channel rotor magnetic pump described in the present invention.

[0025] Figure 2 This is a cross-sectional detail diagram of the counter-rotating flow channel rotor magnetic pump described in the present invention.

[0026] Figure 3 It is a cross-sectional view of the front rotating wheel described in the present invention.

[0027] Figure 4 It is a cross-sectional view of the rear rotating wheel described in the present invention.

[0028] Figure 5 Schematic diagram of the deformation structure of the groove-type flow channel described in the present invention, wherein a is a semicircular arc type; b is a rounded rectangle; c is a semicircular single-side extension type; and d is a helical tooth type.

[0029] In the figure:

[0030] 1-front housing; 2-inlet; 3-front impeller; 4-front coil assembly; 5-outlet; 6-rear housing; 7-rear impeller; 8-rear coil assembly; 9-volute; 10-front sliding sleeve; 11-front coolant inlet; 30-front permanent magnet; 31-W-type flow channel; 32-inlet flow channel; 33-first pair of friction rings; 34-second pair of friction rings; 35-front spiral groove flow channel structure; 351-first stage groove flow channel; 353-third stage 1-stage groove type flow channel; 354-fourth-stage groove type flow channel; 36-front spiral cooling channel; 60-rear sliding sleeve; 61-rear coolant inlet; 70-rear permanent magnet; 71; cooling return hole; 72-guide cone; 73-center flow channel; 74-axial support; 75-rear spiral groove type flow channel structure; 752-second-stage groove type flow channel; 755-fifth-stage groove type flow channel; 76-rear spiral cooling channel; 77-second pair of friction rings. DETAILED DESCRIPTION

[0031] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present invention, and should not be construed as limiting the present invention.

[0032] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "axial", "radial", "vertical", "horizontal", "inner", "outer" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first" and "second" are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, the meaning of "multiple" is two or more, unless otherwise clearly and specifically defined.

[0033] In the present invention, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be an indirect connection through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0034] like Figure 1 and Figure 2 As shown, it includes a housing, a front wheel 3 and a rear wheel 7. The housing includes a front housing 1, a rear housing 6 and a volute 9. The volute 9 connects the front housing 1 and the rear housing 6 to form a closed space. The static connection can effectively avoid leakage. The outlet 5 of the housing is arranged at a certain radial position of the volute 9, and is arranged upward in this embodiment. The inlet 2 of the housing is arranged on the front housing 1; the front wheel 3 is supported inside the front housing 1, and the front wheel 3 is driven to rotate by the front magnetic drive device; the rear wheel 7 is supported inside the rear housing 6, and the rear wheel 7 is driven to rotate in the opposite direction relative to the front wheel 3 by the rear magnetic drive device, that is, the rotation directions of the front wheel 3 and the rear wheel 7 are opposite, and the rotation speeds can be the same or different according to the working conditions. The flow channel surfaces of the front wheel 3 and the rear wheel 7 are respectively provided with spiral flow channels, and one end of the rear wheel 7 is nested in the flow channel of the front wheel 3, which can achieve multi-stage speed-up, so as to ensure that long fibers or high-viscosity fluids can pass smoothly.

[0035] like Figure 2As shown, the front magnetic drive device includes a front permanent magnet 30 and a front coil group 4, a plurality of front permanent magnets 30 are embedded at intervals on the outer periphery of the front wheel 3, and a front coil group 4 is arranged on the side wall of the shell corresponding to the front permanent magnet 30, and the front wheel 3 is rotated by generating a magnetic field by the front coil group 4; the front wheel 3 and the front shell 1 are supported by a front sliding sleeve 10, one end of the front wheel 3 is in contact with the front shell 1 through a second pair of friction rings 34, and the other end of the front wheel 3 is in contact with the volute 9 through a first pair of friction rings 33, and the second pair of friction rings 34 and the first pair of friction rings 33 are used to limit the axial movement of the front wheel 3; a front spiral cooling channel 36 is arranged on the inner side of the front sliding sleeve 10, and a front coolant inlet 11 is provided on the side of the front shell 1, and the front sliding sleeve 10 is cooled by inputting coolant. Several rear permanent magnets 70 are embedded at intervals on the side of the rear wheel 7. A rear coil group 8 is arranged on the side wall of the housing corresponding to the rear permanent magnet 70. The rear wheel 7 is rotated by generating a magnetic field by the rear coil group 8. The rear wheel 7 and the rear housing 6 are supported by a rear sliding sleeve 60. One side of the rear wheel 7 is in contact with the volute 9 through a third pair of friction rings 77. An axial support 74 is arranged between the rear housing 6 and the rear wheel 7. The third pair of friction rings 77 and the axial support 74 are used to limit the axial movement of the rear wheel 7. A rear spiral cooling channel 76 is arranged on the inner side of the rear sliding sleeve 60, and a rear coolant inlet 61 is provided on the side of the rear housing 6 to cool the rear sliding sleeve 60.

[0036] In order to ensure the stability of the wheels and a good heat dissipation effect, the rotation speeds of the front wheel 3 and the rear wheel 7 are controlled between 600 and 1450 rpm. When the viscosity of the transported fluid increases, the rotation speed is reduced.

[0037] The first pair of friction rings 33, the second pair of friction rings 34, the third pair of friction rings 77 and the axial support 74 mentioned above all appear in pairs on the rotating body and the non-rotating body. The front sliding sleeve 10 and the rear sliding sleeve 60 also appear in pairs at the positions where the front rotating wheel 3 and the rear rotating wheel 7 contact the front housing 1 and the rear housing 6. The friction rings are usually made of wear-resistant materials such as silicon carbide, and the sliding sleeves are made of polytetrafluoroethylene (Teflon) hard plastic. In order to make the sliding sleeves stable and not shake, the bearing length L of the rear rotating wheel 7 is 2 0.75 to 1.0 times the length L of the central flow channel 73 1 .

[0038] like Figure 3As shown, the flow channel in the front runner 3 includes a W-shaped flow channel 31 and an inlet flow channel 32 that are interconnected. The inlet flow channel 32 is connected to the shell inlet, and the inlet flow channel 32 is located at the center of the W-shaped flow channel 31. The inlet flow channel 32 is connected to the center of the W-shaped flow channel 31. A front spiral groove type flow channel structure 35 is provided on the flow channel surface of the front runner 3; the rear runner 7 is in a frustum shape, and a central flow channel 73 is provided at the center of the rear runner 7. The central flow channel 73 is nested in the W-shaped flow channel 31, and the inlet flow channel 32 is nested in the central flow channel 73 to divert the central flow channel 73; a rear spiral groove type flow channel structure 75 is provided on the contour of the frustum-shaped rear runner 7, and the contour of the frustum-shaped rear runner 7 includes the surface of the central flow channel 73 and the conical outer side surface of the rear runner 7, as shown in FIG. Figure 4 As shown. A guide cone 72 is provided in the middle of the central flow channel 73 for diverting the fluid in radial direction. Several cooling reflux holes 71 are provided at the root of the guide cone 72 inside the central flow channel 73, so that the coolant entering from the rear coolant inlet 61 can flow into the pump after cooling the rear sliding sleeve 60. The cooling reflux holes 71 are arranged at the root of the guide cone 72 because it is in a low-pressure area, which can prevent the impeller in the pump from flowing back into the gap from the cooling reflux holes 71.

[0039] like Figure 3 As shown, the front spiral groove flow channel structure 35 includes a first-stage groove flow channel 351, a third-stage groove flow channel 353 and a fourth-stage groove flow channel 354. The inner wall of the inlet flow channel 32 is provided with a first-stage groove flow channel 351, and the W-shaped flow channel 31 is provided with a third-stage groove flow channel 353 and a fourth-stage groove flow channel 354, respectively. The third-stage groove flow channel 353 is located on the outer side of the wall of the inlet flow channel 32; the first-stage groove flow channel 351 and the third-stage groove flow channel 353 are horizontal spiral flow channels, that is, the first-stage groove flow channel 351 and the third-stage groove flow channel 353 are located on the inner and outer walls of the inlet flow channel 32, and the fourth-stage groove flow channel 354 is a spiral flow channel that gradually expands along the flow direction. The gradually expanding spiral flow channel angle α of the fourth-stage groove flow channel 354 1 The value range is 20°~50°.

[0040] like Figure 4 As shown, the rear spiral groove flow channel structure 75 includes a second-stage groove flow channel 752 and a fifth-stage groove flow channel 755. The inner wall of the central flow channel 73 is provided with a second-stage groove flow channel 752, and the outer side of the contour of the rear runner 7 is provided with a fifth-stage groove flow channel 755. The second-stage groove flow channel 752 and the fifth-stage groove flow channel 755 are both gradually expanding spiral flow channels along the flow direction. The gradually expanding spiral flow channel angle α of the second-stage groove flow channel 354 2 The value range is 10° to 30°; the outer contour of the rear wheel 7 is an arc shape, and the radius R of the arc outer contour is 1It is 0.4 to 1.0 times the maximum diameter Φ of the rear runner 7.

[0041] like Figure 1 , Figure 3 and Figure 5 As shown, in the embodiment, the liquid medium enters the inlet flow channel 32 and is accelerated by the first-stage groove flow channel 351. Since the inlet flow channel 32 is nested in the central flow channel 73, the liquid medium is diverted at the end of the central flow channel 73; the diverted liquid medium passes through the chamber between the third-stage groove flow channel 353 and the second-stage groove flow channel 752 to achieve the second-stage acceleration, and then passes through the chamber between the fourth-stage groove flow channel 354 and the fifth-stage groove flow channel 755 at the turning point of the W-shaped flow channel 31 to achieve the third-stage acceleration.

[0042] like Figure 5 As shown, the cross section of the spiral flow channel can be a semicircular or rounded rectangular shape. Figure 5 As shown in a and b in the figure; one end of the cross section of the spiral flow channel is provided with a protruding end extending outwards for cutting fibers. In the embodiment, the cross section of the spiral flow channel has a protruding tip extending from one side on the basis of the semicircular cross section. Figure 5 As shown in c; the cross section of the spiral flow channel in the embodiment is a helical tooth type, that is, a protruding tip extends from both ends of the rectangle, Figure 5 As shown in d in the figure; when the fiber is entangled in the impeller, the outer extending protrusion ends of the front impeller and the rear impeller can cut it off, which can effectively prevent the fiber from being entangled in the impeller and avoid blockage of the flow channel.

[0043] like Figure 1 As shown, the arrangement is as shown in the figure. When viewed from the inlet direction, the rotation direction of the front impeller 3 is clockwise, and the rotation direction of the rear impeller 7 is counterclockwise. When the rotation direction changes, the inclination direction of the groove-type flow channel may need to be adjusted.

[0044] It should be understood that although this specification is described according to various embodiments, not every embodiment contains only one independent technical solution. This narrative method of the specification is only for the sake of clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment may also be appropriately combined to form other implementation methods that can be understood by those skilled in the art.

[0045] The series of detailed descriptions listed above are only specific descriptions of feasible embodiments of the present invention. They are not intended to limit the scope of protection of the present invention. All equivalent embodiments or changes that do not deviate from the technical spirit of the present invention should be included in the scope of protection of the present invention.

Claims

1. A counter-rotating flow channel rotor magnetic pump, characterized in that: The invention comprises a housing, a front wheel (3) and a rear wheel (7); the front wheel (3) is supported at the front of the housing and driven to rotate by a front magnetic drive device; the rear wheel (7) is supported at the rear of the housing and driven to rotate in the opposite direction relative to the front wheel (3) by a rear magnetic drive device; the flow channel surfaces of the front wheel (3) and the rear wheel (7) are respectively provided with spiral flow channels; one end of the rear wheel (7) is nested in the flow channel of the front wheel (3) for multi-stage speed increase.

2. The counter-rotating flow channel rotor magnetic pump according to claim 1, characterized in that: The flow channel in the front impeller (3) comprises a W-shaped flow channel (31) and an inlet flow channel (32) which are interconnected, the inlet flow channel (32) being connected to the shell inlet, the inlet flow channel (32) being located at the center of the W-shaped flow channel (31), and a front spiral groove-type flow channel structure (35) being provided on the flow channel surface of the front impeller (3); the rear impeller (7) is in a frustum shape, a central flow channel (73) being provided at the center of the rear impeller (7), the central flow channel (73) being nested in the W-shaped flow channel (31), and the inlet flow channel (32) being nested in the central flow channel (73) for diverting the central flow channel (73); a rear spiral groove-type flow channel structure (75) being provided on the contour of the frustum-shaped rear impeller (7).

3. The counter-rotating flow channel rotor magnetic pump according to claim 2, characterized in that: The front spiral groove flow channel structure (35) comprises a first-stage groove flow channel (351), a third-stage groove flow channel (353) and a fourth-stage groove flow channel (354); the inner wall surface of the inlet flow channel (32) is provided with a first-stage groove flow channel (351); the W-shaped flow channel (31) is provided with a third-stage groove flow channel (353) and a fourth-stage groove flow channel (354); the third-stage groove flow channel (353) is located on the outer side of the wall surface of the inlet flow channel (32); the first-stage groove flow channel (351) and the third-stage groove flow channel (353) are horizontal spiral flow channels, and the fourth-stage groove flow channel (354) is a spiral flow channel that gradually expands along the flow direction.

4. The counter-rotating flow channel rotor magnetic pump according to claim 3, characterized in that: The value range of the gradually expanding spiral flow channel angle α1 of the fourth-stage groove-shaped flow channel (354) is 20° to 50°.

5. The counter-rotating flow channel rotor magnetic pump according to claim 2, characterized in that: The rear spiral groove-shaped flow channel structure (75) comprises a second-stage groove-shaped flow channel (752) and a fifth-stage groove-shaped flow channel (755); the inner wall surface of the central flow channel (73) is provided with a second-stage groove-shaped flow channel (752); the outer side of the contour of the rear impeller (7) is provided with a fifth-stage groove-shaped flow channel (755); the second-stage groove-shaped flow channel (752) and the fifth-stage groove-shaped flow channel (755) are both spiral flow channels that gradually expand along the flow direction.

6. The counter-rotating flow channel rotor magnetic pump according to claim 5, characterized in that: The gradually expanding spiral flow channel angle α2 of the second-stage groove-shaped flow channel (354) ranges from 10° to 30°; the outer contour of the rear impeller (7) is in an arc shape, and the radius R1 of the arc-shaped outer contour is 0.4 to 1.0 times the maximum diameter Φ of the rear impeller (7).

7. The counter-rotating flow channel rotor magnetic pump according to claim 2, characterized in that: The length L2 of the rear impeller (7) supported at the rear of the housing is 0.75 to 1.0 times the length L1 of the central flow channel (73).

8. The counter-rotating flow channel rotor magnetic pump according to any one of claims 1 to 7, characterized in that: One end of the cross section of the spiral flow channel is provided with an outwardly extending protruding end for cutting fibers.

9. The counter-rotating flow channel rotor magnetic pump according to any one of claims 1 to 7, characterized in that: A front permanent magnet (30) is embedded in the front rotating wheel (3), and a front coil group (4) is arranged on the side wall of the shell corresponding to the front permanent magnet (30), and the front rotating wheel (3) is rotated by the front coil group (4) generating a magnetic field; a rear permanent magnet (70) is embedded in the rear rotating wheel (7), and a rear coil group (8) is arranged on the side wall of the shell corresponding to the rear permanent magnet (70), and the rear rotating wheel (7) is rotated by the rear coil group (8) generating a magnetic field; the rotation speed of the front rotating wheel (3) and the rear rotating wheel (7) is 600-1450rpm.

10. The counter-rotating flow channel rotor magnetic pump according to any one of claims 1 to 7, characterized in that: The front rotating wheel (3) is supported at the front of the housing through a front sliding sleeve (10), and a front spiral cooling channel (36) is arranged on the inner side of the front sliding sleeve (10); the rear rotating wheel (7) is supported at the rear of the housing through a rear sliding sleeve (60), and a rear spiral cooling channel (76) is arranged on the inner side of the rear sliding sleeve (60).

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