Disc type rim pump

Abstract

The utility model relates to the technical field of fluid conveying equipment, in particular to a disc type rim pump which comprises a pump shell, a flow channel formed in the pump shell, a guide vane fixed at one end in the flow channel of the pump shell, a hollow shaft arranged at the middle axis of the guide vane, and a power vane rotationally arranged at the other end in the flow channel of the pump shell. A central spindle is arranged at the position of the middle axis of the power blade, the hollow shaft is coaxially and rotatably arranged on the outer side of the central spindle, a stator coil and rotor magnetic steel are arranged on the pump shell and correspondingly distributed in the axial direction of the central spindle, the stator coil is arranged on the outer ring of the guide blade, the rotor magnetic steel is arranged on the outer ring of the power blade, and a detection unit is arranged on the pump shell. Through cooperation of the stator coil and the rotor magnetic steel, on the premise that efficient transmission is ensured, part of axial load is counteracted in a one-way mode through magnetic attraction force, axial limiting friction is reduced, and therefore the probability of axial movement of the rotor is reduced, and the condition of friction collision between the rotor and the stator is avoided.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of fluid conveying equipment, in particular to a disc type rim pump. BACKGROUND

[0002] As a common liquid conveying equipment, axial flow pump is widely used in agricultural irrigation, industrial cooling, urban water supply and other fields. The traditional large flow high-speed axial flow pump usually adopts the mode of direct driving of motor, that is, the motor is placed in the flow channel. This design can effectively transmit power, but there are many limitations in actual application. For example, due to the motor in the middle of the flow channel, the water inlet resistance is large, and the bottom suction cannot be achieved. When the water surface is close to the outer diameter of the pump, it is invalid. Moreover, when connected in series, a large water bag needs to be made to package the motor, and the cable needs to be led out, so that the whole series connection is very heavy.

[0003] In order to overcome the problems of the traditional axial flow pump, the existing solutions mainly include the following ways: one is to optimize the motor arrangement, and move the motor out of the flow channel to reduce the water inlet resistance; the other is to improve the impeller design, and adopt the form of rim pump to improve the low suction performance of the pump.

[0004] Although the above measures improve the working efficiency and reliability of the axial flow pump to some extent, there are still some significant defects. For example, although some existing rim pumps can realize low suction, due to the lack of effective axial limiting mechanism, the rotor is easy to appear axial stringing during use. Since the distance between the rotor magnet steel and the stator coil cannot be too large, because the magnetic force is inversely proportional to the square of the distance, that is, the smaller the gap, the higher the magnetic efficiency. Therefore, when the rotor axially strings, the distance between the rotor magnet steel and the stator coil may increase, which reduces the magnetic efficiency, seriously affects the service life and stability of the pump body. In addition, due to the close distance between the magnet steel and the coil, once the load suddenly changes, such as power failure or water shortage shutdown, friction and collision between the rotor and the stator are easy to occur, which easily causes damage to the rotor or the stator, reduces the reliability and safety of the system. CONTENT OF THE INVENTION

[0005] In order to solve the problem that the rotor and the stator are easy to appear friction and collision when the existing rotor appears axial stringing, and reduce the service life and stability of the pump body while ensuring efficient transmission, the present application provides a disc type rim pump.

[0006] The disc type rim pump provided by the present application adopts the following technical scheme:

[0007] The disc rim pump comprises a pump shell, a flow channel is formed in the pump shell, a guide vane is fixed at one end of the flow channel in the pump shell, a hollow shaft is arranged at the middle axis of the guide vane, a power vane is rotatably arranged at the other end of the flow channel in the pump shell, a mandrel is arranged at the middle axis of the power vane, the hollow shaft is coaxially and rotatably arranged outside the mandrel away from the power vane, a stator coil and a rotor magnetic steel are arranged on the pump shell, the stator coil and the rotor magnetic steel are correspondingly distributed along the axial direction of the mandrel, the stator coil is arranged outside the guide vane, the rotor magnetic steel is arranged outside the power vane, and a detection unit for detecting the actual speed and angle of the rotor magnetic steel is arranged on the pump shell.

[0008] By adopting the above technical scheme, during use, the stator coil outside the guide vane and the rotor magnetic steel outside the power vane are matched, so that only the hollow shaft and the mandrel are arranged in the middle of the flow channel in the pump shell, thereby reducing the internal resistance of the pump shell, ensuring the high-efficiency transmission of the pump body, unidirectionally offsetting part of the axial load through the magnetic attraction force of the stator coil during the operation process, reducing the axial limiting friction, collecting the Hall element data in real time through the external control system, judging the rotor angle and the magnetic pole position, adjusting the coil current and the frequency in real time according to the impeller pressure obtained through the analysis of the corresponding hydraulic model under the rotational speed, changing the coil magnetic attraction force and the angle, so that the impeller rotation is driven while the coil magnetic attraction force is close to the axial load, thereby reducing the axial load at the middle shaft end, even if a power failure or the like occurs, only the axial pressure at the connection position of the hollow shaft and the mandrel is increased, the friction and collision between the rotor and the stator are not caused, and the upward axial magnetic attraction force is formed during the rotation of the rotor magnetic steel driven by the stator coil, which can offset part of the downward axial force caused by the water pressure on the power vane, thereby reducing the axial pressure at the connection position of the hollow shaft and the mandrel, reducing the mechanical wear, and ensuring the service life and stability of the pump body.

[0009] Preferably, the pump shell comprises an outer cylinder shell fixed outside the guide vane, a bottom shell arranged at one end of the outer cylinder shell, and a flange cylinder rotatably arranged between the outer cylinder shell and the bottom shell, an installation groove is formed at one end of the outer cylinder shell facing the flange cylinder, the stator coil is arranged in the installation groove, a flange groove is formed at one end of the flange cylinder facing the outer cylinder shell, the rotor magnetic steel is arranged in the flange groove, the guide vane is fixed to the inner wall of the outer cylinder shell, the power vane is fixed to the inner wall of the flange cylinder, the detection unit is arranged on the bottom shell, and a clamping structure is arranged between the bottom shell and the outer cylinder shell.

[0010] By adopting the above technical scheme, during use, the clamping structure, the pump shell, the outer cylinder shell and the flange cylinder are matched, the detachable connection is realized under the premise of ensuring the normal operation of the rim pump, and the maintenance of the pump body by the staff in the later period is facilitated.

[0011] Preferably, the detection unit comprises a plurality of groups of Hall elements uniformly distributed along the circumference of the flange groove, and the Hall elements are used to detect the position of the rotor magnetic steel in the flange barrel.

[0012] By adopting the technical scheme, when in use, the cooperation of the plurality of groups of Hall elements ensures the accuracy of the detection of the position of the rotor magnetic steel.

[0013] Preferably, the hollow shaft and the mandrel are connected through an oil-free bearing.

[0014] By adopting the technical scheme, when in use, the setting of the oil-free bearing reduces the rotational friction loss and surface wear at the connection between the hollow shaft and the mandrel, while ensuring the stability of the rotation of the power blade.

[0015] Preferably, the mandrel is provided with wear-resistant rings, the two wear-resistant rings are arranged at the two ends of the oil-free bearing, and the mandrel is provided with a positioning structure for positioning the wear-resistant rings.

[0016] By adopting the technical scheme, when in use, the two wear-resistant rings and the oil-free bearing are positioned by the positioning structure, thereby reducing the probability of axial displacement of the oil-free bearing when subjected to axial pressure, and further ensuring that friction and collision do not occur between the rotor and the stator.

[0017] Preferably, the positioning structure comprises an abutment ring fixed to the outer wall of the mandrel and a shaft head cover cap screw-connected to the end of the mandrel close to the hollow shaft, and a positioning groove for positioning the wear-resistant rings and the oil-free bearing is formed between the shaft head end of the shaft head cover cap and the abutment ring.

[0018] By adopting the technical scheme, when in use, the two abutment rings are positioned by the cooperation of the abutment ring and the shaft head cover cap, so that the oil-free bearing is clamped and positioned on the mandrel by the two abutment rings, which is more beneficial to use.

[0019] Preferably, a weight-reducing groove is formed at the end of the mandrel away from the hollow shaft.

[0020] By adopting the technical scheme, when in use, the setting of the weight-reducing groove reduces the weight and production cost of the mandrel.

[0021] Preferably, a flow guide arc surface is arranged at the edge of the pump shell flow passage away from the power blade.

[0022] By adopting the technical scheme, when in use, the flow guide arc surface guides the fluid in the pump shell flow passage, ensuring the efficient transmission of the pump body.

[0023] In summary, the present application has at least one of the following beneficial technical effects:

[0024] 1. By the cooperation of the stator coil of the guide vane outer ring and the rotor magnet of the power vane outer ring, only the hollow shaft and the mandrel are left in the middle of the pump shell flow passage, so as to reduce the internal resistance of the pump shell, ensure the efficient transmission of the pump body, cooperate with the oil-free bearing, and through the magnetic attraction of the stator coil, the part of the axial load is offset in one direction during the operation process, the axial limiting friction is reduced, and the Hall element data is collected in real time through the external control system, the rotor angle and the magnetic pole position are judged, and the impeller pressure obtained by analyzing the corresponding hydraulic model under the speed is used to adjust the coil current and frequency in real time, change the coil magnetic attraction and angle, so that it meets the driving of the impeller rotation while approaching the axial load, thereby reducing the end load of the middle shaft, even if a power failure occurs, only the axial pressure at the connection between the hollow shaft and the mandrel is increased, and friction and collision between the rotor and the stator will not occur. During the rotation of the stator coil driving the rotor magnet, an upward axial magnetic attraction is also formed, which can offset part of the downward axial force on the power vane caused by water pressure, thereby reducing the axial pressure at the connection between the hollow shaft and the mandrel, reducing mechanical wear, and ensuring the service life and stability of the pump body;

[0025] 2. The cooperation of a plurality of groups of Hall elements ensures the accuracy of the detection of the position of the rotor magnet;

[0026] 3. The cooperation of the outer cylinder shell, the bottom shell, the flange cylinder, the clamping structure, the wear-resistant ring, the abutting ring and the shaft head cap realizes the detachable connection of the pump body, thereby facilitating subsequent maintenance. BRIEF DESCRIPTION OF DRAWINGS

[0027] Figure 1 is the axonometric view mainly embodying the overall structure in the first embodiment of the application;

[0028] Figure 2 is the exploded view mainly embodying the overall structure in the first embodiment of the application;

[0029] Figure 3 is the sectional view mainly embodying the overall structure in the first embodiment of the application;

[0030] Figure 4 is the exploded view mainly embodying the positioning structure in the first embodiment of the application;

[0031] Figure 5 is the sectional view mainly embodying the overall structure in the second embodiment of the application;

[0032] Figure 6 is the exploded view mainly embodying the positioning column mounting structure in the second embodiment of the application.

[0033] Label: 1, pump shell; 11, outer cylinder shell; 12, bottom shell; 13, flange cylinder; 14, clamping structure; 141, connecting column; 142, connecting bolt; 15, flow guide camber; 2, flow guide blade; 21, hollow shaft; 22, ring groove; 3, power blade; 31, mandrel; 32, weight-reducing groove; 33, second receiving groove; 34, plugging head; 4, stator coil; 5, rotor magnet steel; 6, Hall element; 7, oil-free bearing; 8, wear-resistant ring; 9, positioning structure; 91, abutting ring; 92, shaft head cap; 10, compression spring; 20, positioning column; 30, return spring; 40, abutting block; 401, first abutting inclined surface; 50, ball; 60, insertion rod; 601, second abutting inclined surface. DETAILED DESCRIPTION

[0034] The following will be described in detail below with reference to the accompanying drawings. Figure 1 - the accompanying drawings Figure 6 The present application will be further described in detail.

[0035] The embodiment of the present application discloses a disc rim pump.

[0036] Embodiment 1:

[0037] Referring to Figure 1 and Figure 2 , a disc rim pump comprises a pump shell 1 arranged horizontally, in this embodiment, the pump shell 1 is in a whole cylindrical shape, a flow channel for fluid passing through is formed in the pump shell 1, the pump shell 1 is composed of an outer cylinder shell 11, a bottom shell 12 and a flange cylinder 13, wherein the flange cylinder 13 is rotationally arranged between the outer cylinder shell 11 and the bottom shell 12, an installation groove is formed at one end of the outer cylinder shell 11 towards the flange cylinder 13, a stator and a stator coil 4 are arranged in the installation groove, and the stator and the stator coil 4 are glued and sealed in the installation groove, a flange groove is formed at one end of the flange cylinder 13 towards the outer cylinder shell 11, a plurality of rotor magnet steels 5 are arranged in the flange groove, the plurality of rotor magnet steels 5 are evenly distributed along the circumferential side of the flange cylinder 13, and the rotor magnet steels 5 are also glued and sealed in the flange groove.

[0038] Referring to Figure 2 and Figure 3 , the stator coil 4 and the rotor magnet steel 5 are correspondingly distributed along the axial direction of the pump shell 1, a flow guide blade 2 is arranged at one end of the outer cylinder shell 11 away from the bottom shell 12, the outer ring of the flow guide blade 2 is fixed to the inner wall of the outer cylinder shell 11, a hollow shaft 21 is integrally formed at the middle axis of the flow guide blade 2, a power blade 3 is arranged in the flow channel of the flange cylinder 13, the outer ring of the power blade 3 is fixed to the inner wall of the flange cylinder 13, a mandrel 31 is integrally formed at the middle axis of the power blade 3, and one end of the mandrel 31 away from the power blade 3 penetrates through the hollow shaft 21, that is, after assembly, the stator coil 4 is located at the outer ring of the flow guide blade 2, and the rotor magnet steel 5 is located at the outer ring of the power blade 3.

[0039] Referring toFigure 2 And Figure 3 In use, the core shaft 31 is supported by the hollow shaft 21, the guide vane 2 and the outer cylinder shell 11, so as to drive the power vane 3 to rotate through the cooperation of the stator coil 4 and the rotor magnetic steel 5. During the rotation of the power vane 3, only the hollow shaft 21 and the core shaft 31 are in the flow passage of the pump shell 1, so as to reduce the internal resistance of the pump shell 1 and ensure the high-efficiency transmission of the pump body. During the rotation of the power vane 3, the magnetic attraction of the stator coil 4 unidirectionally offsets part of the axial load, reduces the axial limiting friction, and the upward axial magnetic attraction formed during the rotation of the rotor magnetic steel 5 driven by the stator coil 4 can offset part of the downward axial force on the power vane 3 caused by the water pressure, so as to reduce the axial pressure at the connection between the hollow shaft 21 and the core shaft 31, reduce the mechanical wear, and ensure the service life and stability of the pump body.

[0040] With reference to Figure 2 And Figure 3 In order to reduce the rotating friction loss and surface wear at the connection between the hollow shaft 21 and the core shaft 31 and ensure the stability of the rotation of the power vane 3, an oil-free bearing 7 is arranged between the hollow shaft 21 and the core shaft 31. The inner wall of the oil-free bearing 7 is nested with the outer wall of the core shaft 31, and the outer wall of the oil-free bearing 7 is nested with the inner wall of the hollow shaft 21. In addition, two wear-resistant rings 8 are arranged on the core shaft 31, the two wear-resistant rings 8 are arranged at the two ends of the oil-free bearing 7, and a positioning structure 9 is arranged on the core shaft 31. In use, the oil-free bearing 7 is axially clamped and positioned by the two wear-resistant rings 8, and the wear-resistant rings 8 are positioned in cooperation with the positioning structure 9, so as to reduce the probability of axial displacement of the oil-free bearing 7 when the oil-free bearing 7 is subjected to axial pressure, and to achieve the purpose of axial limiting of the connection between the hollow shaft 21 and the core shaft 31.

[0041] With reference to Figure 3 And Figure 4 The positioning structure 9 includes an abutting ring 91 and a shaft head cap 92. The abutting ring 91 is integrally formed on the outer wall of the core shaft 31, and the shaft head cap 92 is arranged at the end of the core shaft 31 and is threadedly connected with the end of the core shaft 31. The positioning groove is formed between the shaft head cap 92 and the abutting ring 91, and the wear-resistant ring 8 and the oil-free bearing 7 are located in the positioning groove. In use, the two wear-resistant rings 8 and the oil-free bearing 7 are sequentially installed in the positioning groove, and the oil-free bearing 7 is located between the two wear-resistant rings 8. Then the shaft head cap 92 is screwed on the end of the core shaft 31 until the end of the shaft head cap 92 abuts against the side wall of one of the wear-resistant rings 8. Continue to screw the shaft head cap 92 so that the other wear-resistant ring 8 abuts against the abutting ring 91. Thus, the wear-resistant ring 8 and the oil-free bearing 7 are clamped in the positioning groove through the shaft head cap 92 and the abutting ring 91, and the installation process is simple and convenient.

[0042] With reference to Figure 2 And Figure 3In the process of rotating the power vane 3, the rotation stability of the mandrel 31 is ensured by the wear-resistant ring 8 and the oil-free bearing 7, and the oil-free bearing 7 is provided with axial limiting by the abutting ring 91 and the shaft head cap 92, so as to reduce the axial displacement of the oil-free bearing 7, thereby reducing the relative axial displacement between the mandrel 31 and the hollow shaft 21, and further reducing the friction and collision caused by the increase or decrease of the gap between the stator coil 4 and the rotor magnetic steel 5.

[0043] With reference to Figure 2 And Figure 3 A detection unit is arranged on the side of the bottom shell 12 facing the flange barrel 13, and the detection unit is used to detect the actual speed and angle of rotation of the rotor magnetic steel 5. In the present application, the detection unit is composed of a plurality of groups of Hall elements 6, which are uniformly distributed on the side of the bottom shell 12, and the Hall elements 6 are arranged corresponding to the position of the rotor magnetic steel 5 in the flange barrel 13. When the rotor magnetic steel 5 rotates, the position of the rotor magnetic steel 5 is detected by the plurality of groups of Hall elements 6, so as to detect the actual rotation speed and angle of the rotor magnetic steel 5.

[0044] With reference to Figure 2 And Figure 3 During the operation of the pump body, the relationship between the rotation speed of the rotor magnetic steel 5 and the load is obtained by the external control system according to the hydraulic model analysis data, and the actual speed and angle of the rotor magnetic steel 5 during rotation are detected in real time by the detection unit, so as to adjust the current and frequency of the stator coil 4 in real time, so that the magnetic attraction of the stator coil 4 is always close to the load. In this way, the intermediate shaft end load is reduced. Even if a sudden change such as power failure occurs, the axial pressure of the oil-free bearing 7 will only increase, and the friction and collision between the rotor and the stator will not occur, thereby ensuring the service life of the pump body.

[0045] With reference to Figure 2 And Figure 3 A clamping structure 14 is arranged between the bottom shell 12 and the outer barrel shell 11, so as to realize the detachable connection of the bottom shell 12 and the outer barrel shell 11, thereby facilitating subsequent disassembly and maintenance, and facilitating assembly and processing. The clamping structure 14 includes a connecting column 141 integrally formed on the outer wall of the outer barrel shell 11, and a connecting bolt 142 arranged on the bottom shell 12. The connecting column 141 is provided with a threaded hole at one end facing the bottom shell 12, and the connecting bolt 142 is threadedly connected to the threaded hole after penetrating through the bottom shell 12. In order to ensure the connection stability of the bottom shell 12 and the outer barrel shell 11, a plurality of connecting columns 141 are arranged, and the plurality of connecting columns 141 are uniformly distributed on the outer wall of the outer barrel shell 11.

[0046] With reference to Figure 2 And Figure 3At one end of the mandrel 31 away from the hollow shaft 21, a weight-reducing groove 32 is formed along the axial direction of the mandrel 31. In use, the weight of the mandrel 31 is reduced through the weight-reducing groove 32, the processing cost is saved, and the use is more convenient. In addition, in the present application, a plugging head 34 is threadedly connected to one end of the mandrel 31 close to the bottom shell 12. The plugging head 34 cooperates with the shaft head cover 92 to plug the two ends of the weight-reducing groove 32.

[0047] With reference to Figure 2 and Figure 3 In addition, in the present embodiment, the end of the plugging head 34 away from the mandrel 31 is provided with a circular arc surface, the end of the shaft head cover 92 away from the mandrel 31 is also provided with a circular arc surface, and the flow guide arc surface 15 is formed on the edge of the flow passage of the bottom shell 12 away from the power vane 3. In use, the fluid in the flow passage of the pump shell 1 is guided through the circular arc surfaces of the shaft head cover 92 and the plugging head 34 and the flow guide arc surface 15, thereby ensuring the high transmission efficiency of the pump body.

[0048] The implementation principle of the embodiment of the present application is as follows: in use, the external control system controls the power supply to the stator coil 4 to drive the rotation of the rotor magnetic steel 5. The rotation of the rotor magnetic steel 5 drives the rotation of the power vane 3, thereby realizing the transmission of the pump body. In the working process of the pump body, the actual speed and angle of the rotor magnetic steel 5 are detected in real time by the Hall element 6, and the detection data are transmitted to the external control system. According to the water conservancy model analysis data, the relationship between the rotor magnetic steel 5 speed and the load is known, and the current and frequency of the stator coil 4 are adjusted in real time, so that the magnetic attraction generated by the stator coil 4 is always close to the load, thereby reducing the intermediate shaft end load, reducing the mechanical wear between the hollow shaft 21, the oil-free bearing 7 and the mandrel 31, and ensuring the service life and stability of the pump body.

[0049] The difference between the embodiment 2 and the embodiment 1 is as follows:

[0050] With reference to Figure 5 and Figure 6 A first receiving groove is formed on the side of the abutting ring 91 facing the wear-resistant ring 8, and a compression spring 10 is arranged in the first receiving groove. One end of the compression spring 10 abuts against the bottom wall of the first receiving groove, and the other end of the compression spring 10 abuts against the wear-resistant ring 8. In use, the shaft head cover 92 is screwed to abut against the wear-resistant ring 8 at the end, so as to compress the compression spring 10. After the wear-resistant ring 8 and the oil-free bearing 7 are installed to the specified position, the compression spring 10 is in a compressed state as a whole. Therefore, when the axial force appears between the hollow shaft 21 and the mandrel 31 during the rotation of the power vane 3, the compression spring 10 provides a reverse thrust to the wear-resistant ring 8 and the oil-free bearing 7, thereby further reducing the probability of collision and friction between the stator coil 4 and the rotor magnetic steel 5.

[0051] With reference to Figure 5 and Figure 6Furthermore, in the embodiment, two oil-free bearings 7 can be arranged, and the two oil-free bearings 7 are symmetrically arranged at the axial two ends of the hollow shaft 21, and there is a spacing between the two oil-free bearings 7, and a ring groove 22 is arranged on the inner wall of the hollow shaft 21 corresponding to the spacing, and a plurality of groups of positioning columns 20 are arranged on the mandrel 31 corresponding to the ring groove 22, and the plurality of groups of positioning columns 20 are uniformly distributed along the circumferential side of the mandrel 31, and in the embodiment, the positioning columns 20 are preferably arranged in three groups, and a second receiving groove 33 is arranged on the inner wall of the mandrel 31 corresponding to the ring groove 22, and a return spring 30 is arranged in the second receiving groove 33, and one end of the positioning column 20 is threadedly connected with an abutting block 40, and one end of the return spring 30 abuts against the inner wall of the second receiving groove 33, and the other end of the return spring 30 abuts against the side wall of the abutting block 40.

[0052] With reference to Figure 5 and Figure 6 , the abutting block 40 is located in the lightening groove 32 in the mandrel 31, and the other end of the positioning column 20 extends into the spacing between the two oil-free bearings 7 after penetrating through the side wall of the mandrel 31, and a ball 50 is rotatably arranged on the end of the positioning column 20, and the ball 50 rolls on the inner wall of the ring groove 22, and a first abutting inclined surface 401 is formed on the end of the abutting block 40 away from the positioning column 20, and a plug rod 60 is threadedly connected with the end of the shaft head cover 92 towards the mandrel 31, and the end of the plug rod 60 away from the shaft head cover 92 extends into the lightening groove 32, and a second abutting inclined surface 601 is formed on the end of the plug rod 60 extending into the lightening groove 32, and the first abutting inclined surface 401 and the second abutting inclined surface 601 abut and cooperate.

[0053] With reference to Figure 5 and Figure 6 , in use, after the return spring 30, the positioning column 20 and the abutting block 40 are all assembled on the mandrel 31, without installing the shaft head cover 92, the abutting block 40 is driven to slide along the radial direction of the mandrel 31 by the return spring 30, so as to drive the positioning column 20 and the ball 50 to retract into the mandrel 31, at this time, the installation of the wear-resistant ring 8 and the oil-free bearing 7 is not affected; when the shaft head cover 92 is screwed, and the shaft head cover 92 gradually abuts against the wear-resistant ring 8, the sliding direction of the positioning column 20 is guided through the cooperation of the second abutting inclined surface 601 on the plug rod 60 and the first abutting inclined surface 401 on the abutting block 40, so that the return spring 30 is gradually compressed, so as to drive the positioning column 20 and the ball 50 to gradually extend out of the mandrel 31 and extend into the ring groove 22, until the ball 50 and the side wall of the ring groove 22 abut, so that the hollow shaft 21 is supported and positioned through the positioning column 20, and the friction between the positioning column 20 and the inner wall of the ring groove 22 is reduced through the ball 50, and the rotational friction loss between the mandrel 31 and the hollow shaft 21 is reduced.

[0054] The implementation principle of the embodiment of the application is: in use, the stator coil 4 is controlled to be powered by an external control system to drive the rotation of the rotor magnetic steel 5, the rotation of the rotor magnetic steel 5 drives the rotation of the power vane 3, so that the transmission of the pump body is realized, in the working process of the pump body, the angle and the magnetic pole position of the rotor magnetic steel 5 are collected in real time by the Hall element 6, and the detection data is transmitted to the external control system, the relationship between the rotor magnetic steel 5 speed and the load is obtained according to the impeller pressure obtained by the external control system according to the water conservancy model analysis under the speed, so as to adjust the current and the frequency of the stator coil 4 in real time, change the magnetic attraction force and the angle of the coil, so as to ensure that the magnetic attraction force generated by the stator coil 4 is always close to the load, so as to meet the rotation of the power vane 3 while reducing the intermediate shaft end load, reducing the mechanical wear between the hollow shaft 21, the oil-free bearing 7 and the mandrel 31, and cooperating with the use of the reset spring 30, the positioning column 20, the ball 50 and the compression spring 10, increasing the axial positioning between the hollow shaft 21 and the mandrel 31, further reducing the probability of friction and collision between the stator coil 4 and the rotor magnetic steel 5, so as to ensure the service life and stability of the pump body.

[0055] The above are preferred embodiments of the application, and do not limit the protection scope of the application, therefore: equivalent changes made according to the structure, shape, principle of the application should be covered within the protection scope of the application.

Claims

1. A disc-type rim pump, characterized in that: The pump casing (1) includes a flow channel formed inside the pump casing (1). A guide vane (2) is fixed at one end of the flow channel of the pump casing (1). A hollow shaft (21) is provided at the middle axis of the guide vane (2). A power vane (3) is rotatably provided at the other end of the flow channel of the pump casing (1). A spindle (31) is provided at the middle axis of the power vane (3). The hollow shaft (21) is coaxially rotatably provided on the outer side of the end of the spindle (31) away from the power vane (3). A stator coil (4) and a rotor magnet (5) are provided on the pump casing (1). The stator coil (4) and the rotor magnet (5) are distributed correspondingly along the axial direction of the spindle (31). The stator coil (4) is provided on the outer ring of the guide vane (2). The rotor magnet (5) is provided on the outer ring of the power vane (3). A detection unit for detecting the actual speed and angle of the rotor magnet (5) is provided on the pump casing (1).

2. A disc-type rim pump according to claim 1, characterized in that: The pump casing (1) includes an outer shell (11) fixed to the outer ring of the guide vane (2), a bottom shell (12) disposed at one end of the outer shell (11), and a flange (13) rotatably disposed between the outer shell (11) and the bottom shell (12). The outer shell (11) has an installation groove at the end facing the flange (13), and the stator coil (4) is disposed in the installation groove. The flange (13) has a flange groove at the end facing the outer shell (11), and the rotor magnet (5) is disposed in the flange groove. The guide vane (2) is fixed to the inner wall of the outer shell (11), and the power vane (3) is fixed to the inner wall of the flange (13). The detection unit is disposed on the bottom shell (12), and a snap-fit ​​structure (14) is provided between the bottom shell (12) and the outer shell (11).

3. A disc-type rim pump according to claim 2, characterized in that: The detection unit includes several groups of Hall elements (6) evenly distributed along the circumference of the flange groove. The Hall elements (6) are used to detect the position of the rotor magnet (5) inside the flange cylinder (13).

4. A disc-type rim pump according to claim 1, characterized in that: The hollow shaft (21) and the mandrel (31) are connected by an oil-free bearing (7).

5. A disc-type flange pump according to claim 4, characterized in that: The mandrel (31) is provided with wear-resistant rings (8), and there are two wear-resistant rings (8), which are located at both ends of the oilless bearing (7). The mandrel (31) is provided with a positioning structure (9) for positioning the wear-resistant rings (8).

6. A disc-type rim pump according to claim 5, characterized in that: The positioning structure (9) includes an abutment ring (91) fixed to the outer wall of the mandrel (31) and a shaft head cap (92) threaded to one end of the mandrel (31) near the hollow shaft (21). A positioning groove for positioning the wear-resistant ring (8) and the oil-free bearing (7) is formed between the shaft head end of the shaft head cap (92) and the abutment ring (91).

7. A disc-type rim pump according to claim 1, characterized in that: The mandrel (31) has a weight-reducing groove (32) at the end away from the hollow shaft (21).

8. A disc-type rim pump according to claim 1, characterized in that: The pump casing (1) has a flow guide arc surface (15) on the edge of the flow channel away from the power blade (3).

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