Disc type rim pump

Abstract

The invention 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, and in particular to a disc rim pump. Background Art

[0002] As a common liquid conveying equipment, axial flow pumps are widely used in agricultural irrigation, industrial cooling, urban water supply and other fields. Traditional large-flow and high-speed axial flow pumps are usually driven directly by motors, that is, the motor is placed in the flow channel. This design can effectively transmit power, but there are many limitations in practical applications. For example, because the motor is in the middle of the flow channel, the water inlet resistance is large and it cannot be bottom-sucked. When the water level drops to a level close to the outer diameter of the pump, it fails. In addition, a large water bag needs to be made when connecting in series, and the motor needs to be wrapped in it, and the cables need to be led out, making the entire series connection very bulky.

[0003] In order to overcome the above-mentioned problems of traditional axial flow pumps, existing solutions mainly include the following methods: first, optimize the motor layout, move the motor out of the flow channel, and reduce the water inlet resistance; second, improve the impeller design, adopt the form of a rim pump, and improve the low-suction performance of the pump.

[0004] Although the above measures have improved the working efficiency and reliability of the axial flow pump to a certain extent, there are still some significant defects. For example, although some existing rim pumps can achieve low suction, due to the lack of an effective axial limiting mechanism, the rotor is prone to axial stringing during use. Since the distance between the rotor magnet and the stator coil cannot be too large, and the magnetic force is inversely proportional to the square of the distance, that is, the smaller the gap, the higher the magnetic efficiency, the axial stringing of the rotor may cause the distance between the rotor magnet and the stator coil to increase, thereby reducing the magnetic efficiency and seriously affecting the service life and stability of the pump body; in addition, since the distance between the magnet and the coil is relatively close, once a sudden load change occurs, such as a power outage or water shortage shutdown, friction and collision are likely to occur between the rotor and the stator, which can easily cause damage to the rotor or stator, reducing the reliability and safety of the system. Summary of the invention

[0005] In order to achieve efficient transmission while solving the problem that when the rotor has axial string movement, friction and collision between the rotor and the stator are prone to occur, resulting in reduced service life and stability of the pump body, the present application provides a disc rim pump.

[0006] The present application provides a disc rim pump, which adopts the following technical solution: A disc rim pump comprises a pump casing, a flow channel is formed in the pump casing, a guide vane is fixed at one end of the pump casing flow channel, 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 pump casing flow channel, a core shaft is arranged at the middle axis of the power vane, the hollow shaft is coaxially rotatably arranged on the outside of one end of the core shaft away from the power vane, a stator coil and a rotor magnet are arranged on the pump casing, the stator coil and the rotor magnet are correspondingly distributed along the axial direction of the core shaft, the stator coil is arranged on the outer ring of the guide vane, the rotor magnet is arranged on the outer ring of the power vane, and a detection unit for detecting the actual speed and angle of the rotor magnet is arranged on the pump casing.

[0007] By adopting the above technical solution, when in use, through the cooperation of the stator coil on the outer ring of the guide vane and the rotor magnet on the outer ring of the power blade, there is only the hollow shaft and the core shaft in the middle of the pump casing flow channel, so as to reduce the internal resistance of the pump casing and ensure the efficient transmission of the pump body. During the operation, the magnetic attraction of the stator coil unidirectionally offsets part of the axial load, reduces the axial limit friction, and collects the Hall element data in real time through the external control system to judge the rotor angle and the magnetic pole position, and adjusts the coil current and frequency in real time according to the impeller pressure obtained by the hydraulic model analysis corresponding to the speed, changes the coil magnetic attraction and angle, so that it can meet the driving impeller rotation while approaching the axial load, thereby reducing the load on the intermediate shaft end, even if encountering sudden changes such as power outages, only the axial pressure at the connection between the hollow shaft and the core shaft will be increased, and no friction and collision between the rotor and the stator will be caused. At the same time, the stator coil drives the rotor magnet to rotate, and an upward axial magnetic attraction will be formed, which can offset part of the downward axial force caused by the water pressure on the power blades, thereby reducing the axial pressure at the connection between the hollow shaft and the core shaft, reducing mechanical wear, and ensuring the service life and stability of the pump body.

[0008] Preferably, the pump casing includes an outer cylinder shell fixed to the outer ring of 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, the outer cylinder shell is provided with a mounting groove at one end of the flange cylinder, the stator coil is arranged in the mounting groove, the flange cylinder is provided with a flange groove at one end of the outer cylinder shell, the rotor magnet is arranged in the flange groove, the guide vane is fixed to the inner wall of the outer cylinder shell, the power blade 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.

[0009] By adopting the above technical solution, when in use, through the cooperation of the snap-on structure, pump casing, outer cylinder shell and flange cylinder, a detachable connection is achieved while ensuring the normal operation of the rim pump as a whole, which is convenient for the staff to maintain the pump body in the later stage.

[0010] Preferably, the detection unit comprises a plurality of groups of Hall elements evenly distributed along the circumferential direction of the flange groove, and the Hall elements are used to detect the position of the rotor magnet in the flange cylinder.

[0011] By adopting the above technical solution, when in use, the accuracy of rotor magnetic steel position detection is ensured through the cooperation of several groups of Hall elements.

[0012] Preferably, the hollow shaft and the core shaft are connected via an oil-free bearing.

[0013] By adopting the above technical solution, when in use, the rotational friction loss and surface wear at the connection between the hollow shaft and the core shaft are reduced through the provision of an oil-free bearing, while ensuring the stability of the rotation of the power blades.

[0014] Preferably, a wear-resistant ring is provided on the core shaft, two wear-resistant rings are provided, and the two wear-resistant rings are arranged at both ends of the oil-free bearing, and a positioning structure for positioning the wear-resistant ring is provided on the core shaft.

[0015] By adopting the above technical solution, 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 no friction collision occurs between the rotor and the stator.

[0016] Preferably, the positioning structure includes an abutment ring fixed on the outer wall of the core shaft and a shaft head cap threadedly connected to the end of the core shaft near one end of the hollow shaft, and a positioning groove for positioning the wear-resistant ring and the oil-free bearing is formed between the shaft head end of the shaft head cap and the abutment ring.

[0017] By adopting the above technical solution, when in use, the two abutment rings are positioned through the cooperation of the abutment ring and the shaft head cap, so that the oil-free bearing is clamped and positioned on the core shaft through the two abutment rings, which is more convenient for use.

[0018] Preferably, a weight-reducing groove is provided at one end of the core shaft away from the hollow shaft.

[0019] By adopting the above technical solution, when in use, the weight and production cost of the core shaft are reduced by setting the weight-reducing groove.

[0020] Preferably, a guide camber surface is provided on an edge of one end of the pump casing flow channel away from the power blades.

[0021] By adopting the above technical solution, when in use, the fluid in the flow channel in the pump casing is guided by the guide arc surface, thereby ensuring efficient transmission of the pump body.

[0022] In summary, the present application includes at least one of the following beneficial technical effects: 1. Through the coordination of the stator coil on the outer ring of the guide vane and the rotor magnet on the outer ring of the power blade, there is only the hollow shaft and the core shaft in the middle of the pump casing flow channel, thereby reducing the internal resistance of the pump casing and ensuring the efficient transmission of the pump body. In combination with the oil-free bearing, the magnetic attraction of the stator coil can offset part of the axial load in one direction during operation, reducing the axial limit friction. The Hall element data is collected in real time through the external control system to determine the rotor angle and the magnetic pole position. According to the impeller pressure obtained by the hydraulic model analysis at the corresponding speed, the coil current and frequency are adjusted in real time, and the magnetic attraction and angle of the coil are changed to make it close to the axial load while satisfying the drive impeller rotation, thereby reducing the load on the intermediate shaft end. Even if there is a sudden change such as a power outage, it will only increase the axial pressure at the connection between the hollow shaft and the core shaft, and will not cause friction and collision between the rotor and the stator. At the same time, the stator coil will drive the rotor magnet to rotate, and an upward axial magnetic attraction will be formed, which can offset part of the downward axial force caused by the water pressure on the power blades, thereby reducing the axial pressure at the connection between the hollow shaft and the core shaft, reducing mechanical wear, and ensuring the service life and stability of the pump body. 2. The accuracy of rotor magnetic steel position detection is ensured by using several groups of Hall elements in coordination; 3. Through the cooperation of the outer cylinder shell, the bottom shell, the flange cylinder, the clamping structure, the wear-resistant ring, the abutment ring and the shaft head cap, the detachable connection of the pump body is realized, so as to facilitate the subsequent maintenance. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 It is an axonometric diagram mainly showing the overall structure in the first embodiment of the present application; Figure 2 It is an exploded diagram mainly showing the overall structure in the first embodiment of the present application; Figure 3 It is a cross-sectional view mainly showing the overall structure in the first embodiment of the present application; Figure 4 It is an exploded diagram mainly showing the positioning structure in the first embodiment of the present application; Figure 5 It is a cross-sectional view mainly showing the overall structure in the second embodiment of the present application; Figure 6 It is an exploded view of the positioning column installation structure mainly embodied in the second embodiment of the present application.

[0024] 1. Pump casing; 11. Outer cylinder shell; 12. Bottom shell; 13. Flange cylinder; 14. Clamping structure; 141. Connecting column; 142. Connecting bolt; 15. Guide arc surface; 2. Guide blade; 21. Hollow shaft; 22. Ring groove; 3. Power blade; 31. Core shaft; 32. Weight reduction groove; 33. Second storage groove; 34. Sealing head; 4. Stator coil; 5. Rotor magnet; 6. Hall element; 7. Oil-free bearing; 8. Wear-resistant ring; 9. Positioning structure; 91. Abutment ring; 92. Shaft head cap; 10. Compression spring; 20. Positioning column; 30. Reset spring; 40. Abutment block; 401. First abutment slope; 50. Ball; 60. Insert rod; 601. Second abutment slope. DETAILED DESCRIPTION

[0025] The following is combined with Figure 1 -Attached Figure 6 This application is described in further detail.

[0026] The embodiment of the present application discloses a disc rim pump.

[0027] Embodiment 1: Reference Figure 1 and Figure 2 A disc rim pump comprises a horizontally arranged pump casing 1. In this embodiment, the pump casing 1 is cylindrical as a whole, and a flow channel for fluid to pass through is formed in the pump casing 1. The pump casing 1 consists of an outer cylinder shell 11, a bottom shell 12 and a flange cylinder 13, wherein the flange cylinder 13 is rotatably arranged between the outer cylinder shell 11 and the bottom shell 12, and a mounting groove is opened at one end of the outer cylinder shell 11 facing the flange cylinder 13, and a stator and a stator coil 4 are arranged in the mounting groove, and the stator and the stator coil 4 are sealed in the mounting groove by glue, and a flange groove is opened at one end of the flange cylinder 13 facing the outer cylinder shell 11, and a plurality of rotor magnets 5 are arranged in the flange groove, and the plurality of rotor magnets 5 are evenly distributed along the circumference of the flange cylinder 13, and the rotor magnets 5 are also sealed in the flange groove by glue.

[0028] Reference Figure 2 and Figure 3 The stator coil 4 and the rotor magnet 5 are correspondingly distributed along the axial direction of the pump shell 1. A guide vane 2 is arranged at the end of the outer cylinder shell 11 away from the bottom shell 12. The outer ring of the guide vane 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 guide vane 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 core shaft 31 is integrally formed at the middle axis of the power blade 3. The end of the core shaft 31 away from the power blade 3 is arranged through the hollow shaft 21. The hollow shaft 21 rotates coaxially on the core shaft 31, that is, after assembly, the stator coil 4 is located at the outer ring of the guide vane 2, and the rotor magnet 5 is located at the outer ring of the power blade 3.

[0029] Reference Figure 2and Figure 3 When in use, the core shaft 31 is supported by the hollow shaft 21, the guide vanes 2 and the outer cylinder shell 11, so that the purpose of driving the power blades 3 to rotate is achieved through the cooperation of the stator coil 4 and the rotor magnet 5. During the rotation of the power blades 3, there are only the hollow shaft 21 and the core shaft 31 in the flow channel of the pump casing 1, thereby reducing the internal resistance of the pump casing 1 and ensuring efficient transmission of the pump body; during the rotation of the power blades 3, the magnetic attraction force of the stator coil 4 unidirectionally offsets part of the axial load and reduces the axial limit friction. At the same time, the stator coil 4 drives the rotor magnet 5 to rotate, and an upward axial magnetic attraction force is also formed, which can offset part of the downward axial force caused by the water pressure on the power blades 3, thereby reducing the axial pressure at the connection between the hollow shaft 21 and the core shaft 31, reducing mechanical wear, and ensuring the service life and stability of the pump body.

[0030] Reference Figure 2 and Figure 3 In order to reduce the rotational friction loss and surface wear at the connection between the hollow shaft 21 and the core shaft 31, and at the same time ensure the stability of the rotation of the power blade 3, an oil-free bearing 7 is arranged between the hollow shaft 21 and the core shaft 31, and 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, and the two wear-resistant rings 8 are arranged at both ends of the oil-free bearing 7, and a positioning structure 9 is arranged on the core shaft 31; when in use, the oil-free bearing 7 is axially clamped and positioned by the two wear-resistant rings 8, and then the wear-resistant ring 8 is positioned in cooperation with the positioning structure 9, so as to reduce the probability of axial displacement of the oil-free bearing 7 when it is subjected to axial pressure, thereby achieving the purpose of axially limiting the connection between the hollow shaft 21 and the core shaft 31.

[0031] Reference Figure 3 and Figure 4 The positioning structure 9 includes an abutment ring 91 and a shaft head cap 92. The abutment ring 91 is integrally formed on the outer wall of the core shaft 31. The shaft head cap 92 is arranged at the end of the core shaft 31, and the shaft head cap 92 is threadedly connected to the end of the core shaft 31. A positioning groove is formed between the shaft head cap 92 and the abutment ring 91, and the wear-resistant ring 8 and the oil-free bearing 7 are located in the positioning groove; when in use, the two wear-resistant rings 8 and the oil-free bearing 7 are first installed in the positioning groove in sequence, and the oil-free bearing 7 is located between the two wear-resistant rings 8, and 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 wear-resistant ring 8, and the shaft head cap 92 is continued to be screwed to make the other wear-resistant ring 8 abut against the abutment ring 91, so that 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 abutment ring 91, and the installation process is simple and convenient.

[0032] Reference Figure 2 and Figure 3During the rotation of the power blades 3, the wear-resistant ring 8 and the oil-free bearing 7 ensure the rotation stability of the core shaft 31, and the abutment ring 91 and the shaft head cap 92 provide axial limitation for the oil-free bearing 7, thereby reducing the axial displacement of the oil-free bearing 7, thereby reducing the relative axial displacement between the core shaft 31 and the hollow shaft 21, and further reducing the increase in the gap between the stator coil 4 and the rotor magnet 5 or reducing the friction and collision.

[0033] Reference Figure 2 and Figure 3 A detection unit is provided on the side of the bottom shell 12 facing the flange cylinder 13. The detection unit is used to detect the actual rotation speed and angle of the rotor magnet 5. In the present application, the detection unit is composed of a plurality of groups of Hall elements 6. The plurality of groups of Hall elements 6 are evenly distributed on the circumference of the bottom shell 12, and the Hall elements 6 are arranged corresponding to the position of the rotor magnet 5 in the flange cylinder 13. When the rotor magnet 5 rotates, the plurality of groups of Hall elements 6 cooperate to detect the position of the rotor magnet 5, thereby detecting the actual rotation speed and angle of the rotor magnet 5.

[0034] Reference Figure 2 and Figure 3 During the operation of the pump body, the external control system analyzes the data according to the hydraulic model to obtain the relationship between the rotation speed and load of the rotor magnet 5, and cooperates with the detection unit to detect the actual speed and angle of the rotor magnet 5 in real time, 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, thereby reducing the load on the intermediate shaft end. Even in the event of sudden changes such as power outages, it will only increase the axial pressure of the oil-free bearing 7 without causing friction and collision between the rotor and the stator, thereby ensuring the service life of the pump body.

[0035] Reference Figure 2 and Figure 3 A clamping structure 14 is provided between the bottom shell 12 and the outer cylinder shell 11 to realize the detachable connection between the bottom shell 12 and the outer cylinder shell 11, so as to facilitate the subsequent disassembly and maintenance, and facilitate the assembly and processing. The clamping structure 14 includes a connecting column 141 integrally formed on the outer wall of the outer cylinder 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 one end of the connecting bolt 142 passes through the bottom shell 12 and is threadedly connected to the threaded hole. In order to ensure the connection stability between the bottom shell 12 and the outer cylinder shell 11, a plurality of connecting columns 141 are provided, and the plurality of connecting columns 141 are evenly distributed on the outer wall of the outer cylinder shell 11.

[0036] Reference Figure 2 and Figure 3A weight-reducing groove 32 is provided along the axial direction of the core shaft 31 at one end away from the hollow shaft 21. When in use, the weight of the core shaft 31 is reduced by the weight-reducing groove 32, while saving processing costs and making it more convenient to use. In the present application, a plugging head 34 is threadedly connected to one end of the core shaft 31 close to the bottom shell 12. The plugging head 34 cooperates with the shaft head cap 92 to seal the openings at both ends of the weight-reducing groove 32.

[0037] Reference Figure 2 and Figure 3 In addition, in this embodiment, the end of the plugging head 34 away from the core shaft 31 is set in a circular arc surface, the end of the shaft head cap 92 away from the core shaft 31 is also set in a circular arc surface, and a guide arc surface 15 is formed on the edge of the flow channel at one end of the bottom shell 12 away from the power blade 3; when in use, the fluid in the flow channel of the pump housing 1 is guided by the circular arc surfaces of the shaft head cap 92 and the plugging head 34, as well as the guide arc surface 15, so as to ensure the efficient transmission effect of the pump body.

[0038] The implementation principle of the embodiment of the present application is as follows: when in use, the external control system controls the power supply to the stator coil 4 to drive the rotor magnet 5 to rotate. When the rotor magnet 5 rotates, the power blades 3 are driven to rotate, thereby realizing the transmission of the pump body. During the operation of the pump body, the Hall element 6 detects the actual speed and angle of the rotor magnet 5 in real time, and transmits the detected data to the external control system. The external control system analyzes the data according to the hydraulic model to obtain the relationship between the speed and load of the rotor magnet 5, thereby adjusting the current and frequency of the stator coil 4 in real time, thereby ensuring that the magnetic attraction generated by the stator coil 4 is always close to the load, thereby reducing the load on the intermediate shaft end, reducing the mechanical wear between the hollow shaft 21, the oil-free bearing 7 and the core shaft 31, and ensuring the service life and stability of the pump body.

[0039] The difference between Example 2 and Example 1 is that: Reference Figure 5 and Figure 6 A first receiving groove is provided on the side of the abutment 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; when in use, the shaft head cap 92 is screwed to make the end of the shaft head cap 92 abut against the wear-resistant ring 8, thereby compressing the compression spring 10 until the wear-resistant ring 8 and the oil-free bearing 7 are installed to the specified position, and 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 core shaft 31 during the rotation of the power blade 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 magnet 5.

[0040] Reference Figure 5 and Figure 6In addition, in the present embodiment, two oil-free bearings 7 can be provided, and the two oil-free bearings 7 are symmetrically arranged at the axial ends of the hollow shaft 21, and there is a spacing between the two oil-free bearings 7. An annular groove 22 is provided on the inner wall of the hollow shaft 21 corresponding to the spacing, and a plurality of groups of positioning columns 20 are provided on the core shaft 31 corresponding to the annular groove 22. The plurality of groups of positioning columns 20 are evenly distributed along the circumference of the core shaft 31. In the present embodiment, the positioning columns 20 are preferably provided in three groups, and a second receiving groove 33 is provided on the inner wall of the core shaft 31 corresponding to the annular groove 22. A return spring 30 is provided in the second receiving groove 33. One end of the positioning column 20 is threadedly connected to an abutment 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 abutment block 40.

[0041] Reference Figure 5 and Figure 6 The abutment block 40 is located in the weight-reducing groove 32 in the core shaft 31, and the other end of the positioning column 20 passes through the side wall of the core shaft 31 and extends into the gap between the two oil-free bearings 7. A ball 50 is rotatably arranged at the end of the positioning column 20, and the ball 50 rolls on the inner wall of the annular groove 22. A first abutment slope 401 is formed at the end of the abutment block 40 away from the positioning column 20, and an insertion rod 60 is threadedly connected to the end of the shaft head cap 92 facing the core shaft 31. The end of the insertion rod 60 away from the shaft head cap 92 extends into the weight-reducing groove 32, and a second abutment slope 601 is formed at the end of the insertion rod 60 extending into the weight-reducing groove 32, and the first abutment slope 401 abuts and cooperates with the second abutment slope 601.

[0042] Reference Figure 5 and Figure 6 When in use, after the return spring 30, the positioning column 20, and the abutment block 40 are all assembled on the core shaft 31, without installing the shaft head cap 92, the return spring 30 drives the abutment block 40 to slide radially along the core shaft 31, thereby driving the positioning column 20 and the ball 50 to retract into the core shaft 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 cap 92 is screwed so that the shaft head cap 92 gradually abuts against the wear-resistant ring 8, the second abutment slope 601 on the plug rod 60 and the abutment block The cooperation of the first abutment slope 401 on 40 realizes the guidance of the sliding direction of the positioning column 20, so that the return spring 30 is gradually compressed to drive the positioning column 20 and the ball 50 to gradually extend out of the core shaft 31 and extend into the annular groove 22 until the ball 50 abuts against the side wall of the annular groove 22, thereby supporting and positioning the hollow shaft 21 through the positioning column 20, and at the same time reducing the friction between the positioning column 20 and the inner wall of the annular groove 22 through the ball 50, thereby reducing the rotational friction loss between the core shaft 31 and the hollow shaft 21.

[0043] The implementation principle of the embodiment of the present application is as follows: when in use, the external control system controls the stator coil 4 to be energized to drive the rotor magnet 5 to rotate. When the rotor magnet 5 rotates, the power blade 3 is driven to rotate, thereby realizing the transmission of the pump body. During the operation of the pump body, the angle and magnetic pole position of the rotor magnet 5 are collected in real time by the Hall element 6, and the detection data is transmitted to the external control system. The impeller pressure obtained by the external control system according to the corresponding hydraulic model analysis at the speed is known, and the relationship between the speed and load of the rotor magnet 5 is obtained, so as to adjust the current and frequency of the stator coil 4 in real time, change the magnetic attraction force and 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, thereby satisfying the driving power blade 3 to rotate while reducing the load on the intermediate shaft end, reducing the mechanical wear between the hollow shaft 21, the oil-free bearing 7 and the core shaft 31, and at the same time, with the use of the reset spring 30, the positioning column 20, the ball 50, and the compression spring 10, the axial positioning between the hollow shaft 21 and the core shaft 31 is increased, and the probability of friction and collision between the stator coil 4 and the rotor magnet 5 is further reduced, thereby ensuring the service life and stability of the pump body.

[0044] The above are all preferred embodiments of the present application, and the protection scope of the present application is not limited thereto. Therefore, any equivalent changes made according to the structure, shape, and principle of the present application should be included in the protection scope of the present application.

Claims

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

2. A disc rim pump according to claim 1, characterized in that: The pump housing (1) comprises an outer cylinder shell (11) fixed to the outer ring of the guide vane (2), a bottom shell (12) arranged at one end of the outer cylinder shell (11), and a flange cylinder (13) rotatably arranged between the outer cylinder shell (11) and the bottom shell (12); the outer cylinder shell (11) is provided with a mounting groove at one end facing the flange cylinder (13); the stator coil (4) is arranged in the mounting groove; the flange cylinder (13) is provided with a flange groove at one end facing the outer cylinder shell (11); the rotor magnet (5) is arranged in the flange groove; the guide vane (2) is fixed to the inner wall of the outer cylinder shell (11); the power vane (3) is fixed to the inner wall of the flange cylinder (13); the detection unit is arranged on the bottom shell (12); and a clamping structure (14) is arranged between the bottom shell (12) and the outer cylinder shell (11).

3. A disc rim pump according to claim 2, characterized in that: The detection unit comprises a plurality of groups of Hall elements (6) uniformly distributed along the circumference of the flange groove, and the Hall elements (6) are used to detect the position of the rotor magnet (5) in the flange cylinder (13).

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

5. A disc rim pump according to claim 4, characterized in that: The core shaft (31) is provided with a wear-resistant ring (8), two wear-resistant rings (8) are provided, and the two wear-resistant rings (8) are arranged at both ends of the oil-free bearing (7), and the core shaft (31) is provided with a positioning structure (9) for positioning the wear-resistant ring (8).

6. A disc rim pump according to claim 5, characterized in that: The positioning structure (9) comprises an abutment ring (91) fixed to the outer wall of the core shaft (31), and a shaft head cap (92) threadedly connected to one end of the core shaft (31) close to the hollow shaft (21), and 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 rim pump according to claim 1, characterized in that: The core shaft (31) is provided with a weight-reducing groove (32) at one end away from the hollow shaft (21).

8. A disc rim pump according to claim 1, characterized in that: A flow guide cambered surface (15) is provided at an edge of one end of the flow channel of the pump housing (1) away from the power blades (3).

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