Axial flow blade and guide vane for submersible pump and submersible pump

Abstract

The invention relates to the technical field of emergency rescue and fire fighting, and discloses an axial flow blade and a guide blade for a submersible pump and the submersible pump, and the blade and the guide blade of the axial flow submersible pump are matched to form a blade-guide blade group; the blade is divided into N sections of blade sections, and the stacking line of the blade is determined by combining the N sections of blade sections, the outer section of a hub of the impeller where the blade is located and the curved surface extension stacking point of the outer section of the impeller; the guide vane is divided into N sections of guide vane sections, and the stacking line of the guide vane is determined by the combination of the N sections of guide vane sections, the outer section of a hub of the guide vane and the curved surface extension stacking point of the outer section of the guide vane. A blade-guide blade set with the length shorter than that of blades and guide blades of an original submersible pump is adopted, the stacking lines of the guide blades and the blades are determined through the combination of the sections of the multiple sections of guide blades and the blades, the outer section of a hub and the curved surface extension stacking points of the outer section, and the main body shapes of the guide blades and the blades are determined so as to meet the operation requirements of lift and flow. Meanwhile, the overall weight of the submersible pump is reduced in the pump body direction, and carrying difficulty is reduced.

Description

Technical Field

[0001] The present application relates to the technical field of emergency rescue and fire fighting, and in particular to axial flow blades and guide vanes for submersible pumps and submersible pumps. Background Art

[0002] Submersible pumps can work semi-submerged or fully submerged in water and can be used in emergency rescue, fire fighting, agricultural irrigation, emergency rescue and other fields.

[0003] Submersible electric pumps are a combination of a pump body and a motor. They are widely used in emergency rescue and firefighting. The motor of a submersible electric pump will be sealed, and the motor as a whole can be placed in water to work. The motor drives the impeller at the water inlet of the pump body to rotate. The impeller blades rotate to suck liquid from the water inlet of the pump body and push it to the water outlet of the pump body. The liquid is then guided by the guide vanes at the water outlet of the pump body and pumped out.

[0004] When using submersible electric pumps in the fields of emergency rescue and firefighting, the submersible electric pumps need to be frequently moved. However, the pump body and motor combination of existing submersible electric pumps are heavy, which is not convenient for users to carry. Frequent carrying will cause excessive fatigue of personnel, and even cause problems such as work injuries to personnel and damage to equipment during transportation. Such problems in emergency rescue operations and firefighting operations are likely to cause serious consequences. Summary of the invention

[0005] In order to solve the problem that the pump body and motor combination of the existing submersible pump is heavy and inconvenient for operators to carry, the present application provides axial flow blades and guide vanes for a submersible pump and a submersible pump.

[0006] In the first aspect, the present application provides axial flow blades and guide vanes for a submersible pump, which adopt the following technical solutions: Axial flow blades and guide vanes for submersible pumps include blades and guide vanes with shortened lengths, wherein the blades and guide vanes cooperate to form a blade-guide vane group with shortened lengths; the blades are divided into N blade cross sections in the radial direction of the impeller hub, and the stacking line of the blades is determined by a combination of N blade cross sections, an outer cross section of the impeller hub where the blades are located, and a curved surface extension stacking point combination of the outer cross section of the impeller; the guide vanes are divided into N guide vane cross sections in the radial direction of the guide vane hub, and the stacking line of the guide vanes is determined by a combination of N guide vane cross sections, an outer cross section of the guide vane hub, and a curved surface extension stacking point combination of the outer cross section of the guide vane.

[0007] By adopting the above technical scheme, a blade-guide vane group whose length is shorter than that of the blades and guide vanes of the original submersible pump is used, and the stacking lines of the guide vanes and blades are determined by combining the curved extension stacking points of multiple guide vane and blade cross sections, the guide vanes and blade hub outer cross sections, and the guide vanes and blade outer cross sections, thereby determining the main shape of the guide vanes and blades, thereby meeting the operational requirements of head and flow, and at the same time reducing the overall weight of the submersible pump from the pump body direction, thereby reducing the difficulty of handling.

[0008] Preferably, the guide vane is divided into six sections of guide vane cross-sections in the radial direction of the guide vane hub, the first guide vane cross-section R83.6, angle 1 is 48.5°, angle 2 is 36.23°, and the projection arc range is -23.39° to 17.31°; the second guide vane cross-section R75.54, angle 1 is 50.61°, angle 2 is 40.99°, and the projection arc range is -24.15° to 17.35°; the third guide vane cross-section R67.47, angle 1 is 52.84°, angle 2 is 47.03°, and the projection arc range is -25.11° to 17.4°; the fourth guide vane cross-section R59.4, angle 1 is 55 .6°, angle 2 is 52.9°, and the projected arc range is -26.37° to 17.46°; the fifth guide vane section is R51.32, angle 1 is 58.81°, angle 2 is 58.81°, and the projected arc range is -28.09° to 17.56°; the sixth guide vane section is R43.25, angle 1 is 62.94°, angle 2 is 62.94°, and the projected arc range is -30.57° to 17.7°; the hub outer section of the guide vane is R35, and the outer section of the guide vane is R86.5; the combination of the curved surface extension points of the guide vane section and the parameters of the six sections of the guide vane section, The guide vane hub outer section parameters and the range of the guide vane outer section parameters determine the guide vane stacking line; the blade is divided into six blade sections in the radial direction of the blade hub, the first blade section is R83.13, the angle is 30.99°, and the projection arc range is -42.67° to 39.27°; the second blade section is R75.1, the angle is 33.61°, and the projection arc range is -43.6° to 39.86°; the third blade section is R67.08, the angle is 36.62°, and the projection arc range is -44.78° to 40.68°; the fourth blade section is R59.05, the angle is 40.31°, and the projection arc range is The range is -46.33° to 41.66°; the fifth blade section is R51.03, the angle is 44.45°, and the projected arc range is -48.45° to 42.97°; the sixth blade section is R43, the angle is 49.35°, and the projected arc range is -51.54° to 45.31°; the hub outer section of the impeller where the blade is located is R35, and the outer section of the impeller where the blade is located is R86; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the blade section and the parameters of the six blade sections, the hub outer section parameters of the impeller where the blade is located, and the outer section parameters of the impeller where the blade is located.

[0009] Preferably, the guide vane is divided into six sections of guide vane cross-sections in the radial direction of the guide vane hub. The first guide vane cross-section is R104.9, the angle θ is 46.36°, and the projected arc range is -18.4° to 17.88°; the second guide vane cross-section is R94.76, the angle θ is 49.19°, and the projected arc range is -18.39° to 18.04°; the third guide vane cross-section is R84.63, the angle θ is 52.24°, and the projected arc range is -18.38° to 18.25°; the fourth guide vane blade cross-section is R74.5, the angle θ is 55.58°, and the projected arc range is -18. 37° to 18.54°; the fifth guide vane blade section is R64.38, the angle θ is 59.18°, and the projection arc range is -18.37° to 18.92°; the sixth guide vane blade section is R54.25, the angle θ is 63.09°, and the projection arc range is -18.38° to 19.42°; the hub outer section of the guide vane is R49, and the outer section of the guide vane is R108.5; the guide vane overlap is determined by the combination of the curved surface extension overlap points of the guide vane section and the parameters of the six sections of the guide vane section, the hub outer section parameters of the guide vane, and the range of the outer section parameters of the guide vane The blade is divided into six blade sections in the radial direction of the blade hub. The first blade section is R104.4, the angle is 19.34°, and the projected arc range is -42.69° to 35.81°; the second blade section is R94.32, the angle is 22.2°, and the projected arc range is -43.87° to 37.16°; the third blade section is R84.24, the angle is 25.67°, and the projected arc range is -45.15° to 38.79°; the fourth blade section is R74.16, the angle is 29.88°, and the projected arc range is -46.53° to 40. 73°; the fifth blade section is R64.08, the angle is 35.05°, and the projected arc range is -47.87° to 43.03°; the sixth blade section is R54, the angle is 41.34°, and the projected arc range is -48.98° to 45.67°; the hub outer section of the impeller where the blade is located is R49, and the outer section of the impeller where the blade is located is R108; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the blade section and the parameters of the six blade sections, the hub outer section parameters of the impeller where the blade is located, and the outer section parameters of the impeller where the blade is located.

[0010] Preferably, the guide vane is divided into six sections of guide vane cross-sections in the radial direction of the guide vane hub, the first guide vane cross-section R112.62, θ is 64.32°, and the projected arc range is -18.4° to 17.13°; the second guide vane cross-section R101.74, θ is 60.45°, and the projected arc range is -18.39° to 17.37°; the third guide vane cross-section R90.87, θ is 56.92°, and the projected arc range is -18.38° to 17.67°; the fourth guide vane cross-section R80, θ is 53.67°, and the projected arc range is -18.38° to 18 .04°; the fifth guide vane section is R69.12, θ is 50.68°, and the projected arc range is -18.38° to 18.48°; the sixth guide vane section is R58.25, θ is 47.93°, and the projected arc range is -18.38° to 19.07°; the hub outer section of the guide vane is R54.5, and the outer section of the guide vane is R116.5; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the guide vane section and the parameters of the six sections of the guide vane section, the hub outer section parameters of the guide vane, and the range of the outer section parameters of the guide vane; the blade is at The blade hub radius direction is divided into six blade sections. The first blade section is R112.13, θ is 22.63°, and the projection arc range is -36.45° to 38.88°; the second blade section is R101.31, the angle is 25.59°, and the projection arc range is -38.08° to 38.48°; the third blade section is R90.48, the angle is 28.9°, and the projection arc range is -39.81° to 38.16°; the fourth blade section is R79.65, the angle is 32.92°, and the projection arc range is -41.72° to 38.08 °; the fifth blade section is R68.83, the angle is 37.52°, and the projected arc range is -43.89° to 38.47°; the sixth blade section is R58, the angle is 42.8°, and the projected arc range is -46.53° to 39.7°; the hub outer section of the impeller where the blade is located is R54, and the outer section of the impeller where the blade is located is R116; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the blade section and the parameters of the six blade sections, the hub outer section parameters of the impeller where the blade is located, and the outer section parameters of the impeller where the blade is located.

[0011] In the second aspect, the present application provides a submersible pump, which adopts the following technical solution: A submersible pump comprises a pump body and a motor, wherein the pump body is provided with axial flow blades and guide vanes for the submersible pump, the motor is drivingly connected to the blades, the motor comprises a stator and a rotor, a plurality of groups of magnetic steel grooves are evenly provided along the circumferential direction near the outer circle of the rotor, and the magnetic steel grooves are provided with magnetic steel sheets; By adopting the above technical solution, the arrangement position and number of the magnetic steel slots on the rotor are optimized, that is, the arrangement position and number of the magnetic steel sheets are optimized, the space utilization rate of the rotor is improved, and the number of arranged magnetic steel sheets is increased. As a result, the number of arranged magnetic steel sheets can be increased while reducing the length of the magnetic steel sheets, and the working requirements of the motor of the submersible pump can still be met, thereby achieving the purpose of reducing the overall weight of the submersible pump from both the pump body and the motor, making it easier for users to carry it.

[0012] Preferably, a sealed chamber is formed in the casing of the motor, the chamber is used to install the stator and the rotor, and lubricating oil is injected into the chamber.

[0013] By adopting the above technical solution, the lubricating oil can not only play a lubricating role, but also a cooling role, especially in the working environment where the submersible pump needs to be started and stopped frequently, it has a good heat dissipation effect.

[0014] Preferably, an oil filling hole is provided on the bottom surface of the casing of the motor, and a sealing member is provided on the oil filling hole.

[0015] By adopting the above technical solution, lubricating oil can be added to the chamber through the oil filling hole on the bottom surface of the motor casing, which has good operability.

[0016] Preferably, the injection height of the lubricating oil liquid in the chamber does not exceed one third of the chamber height.

[0017] By adopting the above technical solution, the filling amount of the lubricating oil in the chamber is limited to avoid affecting the normal operation of the motor stator and rotor, while still achieving a good heat dissipation effect.

[0018] Preferably, the pump body includes a pump casing and a water inlet joint, the pump casing is connected to the casing of the motor through the water inlet joint, and the casing of the motor and the water inlet joint are integrally arranged.

[0019] By adopting the above technical solution, the motor casing and the water inlet section are manufactured in one piece, which is beneficial to improving the structural strength and stability of the connection between the pump body and the motor and is easy to carry.

[0020] Preferably, the pump casing is detachably connected to the water inlet section, the blades are drivingly connected to the pump shaft of the motor and are placed in the water inlet section, and the guide vanes are fixedly arranged at the water outlet of the pump casing.

[0021] By adopting the above technical scheme, on the basis of the integral connection between the water inlet section and the motor casing, the overall disassembly and installation of the guide vane and the pump casing can be further realized, and the blades can be disassembled and installed separately, thereby realizing the combined installation and disassembly of the blades and guide vanes.

[0022] Preferably, the water inlet section is provided with a hook structure, and the water inlet section is hung with a mesh cover via the hook structure, and the mesh cover covers the water inlet of the water inlet section.

[0023] By adopting the above technical solution, the mesh cover can prevent debris in the water from entering the pump body, ensuring the normal operation of the submersible pump. At the same time, the mesh cover and the water inlet section are connected by a hook structure, which has good operability.

[0024] Preferably, the water outlet of the pump body is connected to a water outlet pipe, and the water outlet pipe is detachably connected to the water outlet of the pump body.

[0025] By adopting the above technical solution, the water outlet pipe and the pump body are detachably connected, which is convenient for quick disassembly, assembly and replacement during operation and has good practicality.

[0026] In summary, the present application includes at least one of the following beneficial technical effects: 1. Use a shorter blade-guide vane group to replace the blades and guide vanes of the original submersible pump, and use the multi-section guide vane and blade cross-section, the hub outer cross-section and the outer cross-section curved surface extension stacking point combination to determine the stacking line of the guide vane and blade, thereby determining the main shape of the guide vane and blade, thereby meeting the operation requirements of head and flow, while reducing the overall weight of the submersible pump and reducing the difficulty of handling; 2. Make full use of the available space of the rotor and increase the number of magnetic steel sheets arranged on the rotor. While reducing the length of the magnetic steel sheets, increasing the number of magnetic steel sheets arranged can still meet the working requirements of the motor of the submersible pump, thereby achieving the purpose of reducing the overall weight of the submersible pump and facilitating the handling of operators; 3. Optimize the connection structure between the pump body and the motor of the submersible pump, realize the integrated connection between the motor and the water inlet section of the pump body, and meet the requirements for the matching combination installation of the pump body blades and guide vanes; 4. Inject lubricating oil into the chamber of the motor where the stator and rotor are located to improve the cooling and heat dissipation effect of the submersible pump and realize the oil replenishment operation at the same time. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 is a schematic diagram of the cross-sectional parameters of the guide vane in the first embodiment; Figure 2 is a schematic diagram of angle and radian parameters of the first guide vane in the first embodiment; Figure 3 is a schematic diagram of angle and radian parameters of the second guide vane in the first embodiment; Figure 4 is a schematic diagram of angle and radian parameters of the third guide vane in the first embodiment; Figure 5 is a schematic diagram of angle and radian parameters of the fourth guide vane in the first embodiment; Figure 6is a schematic diagram of angle and radian parameters of the fifth guide vane in the first embodiment; Figure 7 is a schematic diagram of angle and radian parameters of the sixth guide vane in the first embodiment; Figure 8 is a schematic diagram of the cross-sectional parameters of the blade in the first embodiment; Fig. 9 is a schematic diagram of angle and radian parameters of the first blade in the first embodiment; Fig.10 is a schematic diagram of angle and curvature parameters of the second blade in the first embodiment; Fig.11 is a schematic diagram of angle and radian parameters of the third blade in the first embodiment; Fig.12 is a schematic diagram of angle and radian parameters of the fourth blade in the first embodiment; Fig.13 is a schematic diagram of angle and radian parameters of the fifth blade in the first embodiment; Fig.14 is a schematic diagram of angle and radian parameters of the sixth blade in the first embodiment; Fig.15 is a schematic diagram of the cross-sectional parameters of the guide vane in the second embodiment; Fig.16 is a schematic diagram of the angle and radian parameters of the first guide vane in the second embodiment; Fig.17 is a schematic diagram of the angle and radian parameters of the second guide vane in the second embodiment; Fig.18 is a schematic diagram of angle and radian parameters of the third guide vane in the second embodiment; Fig.19 is a schematic diagram of angle and radian parameters of the fourth guide vane in the second embodiment; Fig. 20 is a schematic diagram of the angle and radian parameters of the fifth guide vane in the second embodiment; Fig.21 is a schematic diagram of angle and radian parameters of the sixth guide vane in the second embodiment; Fig. 22 is a schematic diagram of the cross-sectional parameters of the blade in the second embodiment; Fig.23 is a schematic diagram of angle and radian parameters of the first blade in the second embodiment; Fig.24 is a schematic diagram of the angle and curvature parameters of the second blade in the second embodiment; Fig.25 is a schematic diagram of angle and radian parameters of the third blade in the second embodiment; Fig.26 is a schematic diagram of angle and radian parameters of the fourth blade in the second embodiment; Fig. 27 is a schematic diagram of the angle and radian parameters of the fifth blade in the second embodiment; Fig.28 is a schematic diagram of angle and radian parameters of the sixth blade in the second embodiment; Fig.29 is a schematic diagram of the cross-sectional parameters of the guide vane in the third embodiment; Fig.30 is a schematic diagram of angle and radian parameters of the first guide vane in Embodiment 3; Fig.31 is a schematic diagram of angle and radian parameters of the second guide vane in Embodiment 3; Fig.32 is a schematic diagram of angle and radian parameters of the third guide vane in the third embodiment; Fig.33 is a schematic diagram of angle and radian parameters of the fourth guide vane in the third embodiment; Fig.34 is a schematic diagram of the angle and radian parameters of the fifth guide vane in the third embodiment; Fig.35 is a schematic diagram of angle and radian parameters of the sixth guide vane in the third embodiment; Fig.36 is a schematic diagram of the cross-sectional parameters of the blade in the third embodiment; Fig.37 is a schematic diagram of angle and radian parameters of the first blade in Embodiment 3; Fig.38 is a schematic diagram of the angle and curvature parameters of the second blade in the third embodiment; Fig.39 is a schematic diagram of angle and radian parameters of the third blade in the third embodiment; Fig.40 is a schematic diagram of angle and radian parameters of the fourth blade in the third embodiment; Fig.41 is a schematic diagram of the angle and curvature parameters of the fifth blade in the third embodiment; Fig.42 is a schematic diagram of angle and radian parameters of the sixth blade in the third embodiment; Fig.43 It is a schematic diagram of the overall structure of the submersible pump in the implementation of this application; Fig.44 is a schematic cross-sectional diagram of a submersible pump in an embodiment of the present application; Fig.45 yes Fig.44 The enlarged schematic diagram of the middle A part; Fig.46 It is a schematic diagram of the installation structure of the cable oil seal in the second embodiment of the present application.

[0028] Explanation of the reference numerals: 1. Pump body; 11. Pump casing; 12. Water inlet section; 2. Motor; 21. Chamber; 22. Connecting tube shell; 221. Inner tube structure; 222. Outer tube structure; 223. Sealing ring; 224. Sealing gasket; 225. Elastic compensation structure one; 226. Elastic compensation structure two; 3. Hook structure; 4. Net cover; 5. Cable oil seal. DETAILED DESCRIPTION

[0029] The following is combined with Figure 1-Figure 46 This application is described in further detail.

[0030] The embodiments of the present application disclose axial flow blades and guide vanes for a submersible pump.

[0031] Example 1 Axial flow blades and guide vanes for submersible pumps include blades and guide vanes with shortened lengths, wherein the blades and guide vanes cooperate to form a blade-guide vane group with shortened lengths; the blades are divided into N sections of blade cross-sections in the radial direction of the impeller hub, and the stacking line of the blades is determined by a combination of N sections of blade cross-sections, an outer section of the impeller hub where the blades are located, and a curved surface extension stacking point combination of the outer section of the impeller; the guide vanes are divided into N sections of guide vane cross-sections in the radial direction of the guide vane hub, and the stacking line of the guide vanes is determined by a combination of N sections of guide vane cross-sections, an outer section of the guide vane hub, and a curved surface extension stacking point combination of the outer section of the guide vane.

[0032] Combination Figure 1-Figure 7As shown, the guide vane angle on the six-section guide vane cross section is θ, and the change of the angle θ of the guide vane cross section rotates with span = (5.58, -7.43) as the rotation center point, and the guide vane blade cross section is defined by the radius. The guide vane is divided into six sections in the radial direction of the guide vane hub. The first guide vane section is R83.6, angle 1 is 48.5°, angle 2 is 36.23°, and the projection arc range is -23.39° to 17.31°; the second guide vane section is R75.54, angle 1 is 50.61°, angle 2 is 40.99°, and the projection arc range is -24.15° to 17.35°; the third guide vane section is R67.47, angle 1 is 52.84°, angle 2 is 47.03°, and the projection arc range is -25.11° to 17.4°; the fourth guide vane section is R59.4, angle 1 is 55.6°, angle 2 is 52.9 °, the projection arc range is -26.37° to 17.46°; the fifth guide vane section is R51.32, angle 1 is 58.81°, angle 2 is 58.81°, and the projection arc range is -28.09° to 17.56°; the sixth guide vane section is R43.25, angle 1 is 62.94°, angle 2 is 62.94°, and the projection arc range is -30.57° to 17.7°; the hub outer section of the guide vane is R35, and the outer section of the guide vane is R86.5; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the guide vane section and the range of the six-segment guide vane section parameters, the guide vane hub outer section parameters, and the guide vane outer section parameters.

[0033] Combination Figure 8-Figure 14As shown, the blade is divided into six blade sections in the radial direction of the blade hub. The blade angles on the six blade sections are θ. The change in the angle θ of the blade section is rotated with span = (2.95, -9.29) as the rotation center point, and the blade section is defined by the radius. The first blade section is R83.13, the angle is 30.99°, and the projected arc range is -42.67° to 39.27°; the second blade section is R75.1, the angle is 33.61°, and the projected arc range is -43.6° to 39.86°; the third blade section is R67.08, the angle is 36.62°, and the projected arc range is -44.78° to 40.68°; the fourth blade section is R59.05, the angle is 40.31°, and the projected arc range is -46.33° to 41.66°; the fifth The blade section is R51.03, the angle is 44.45°, and the projection arc range is -48.45° to 42.97°; the sixth blade section is R43, the angle is 49.35°, and the projection arc range is -51.54° to 45.31°; the outer section of the hub of the impeller where the blade is located is R35, and the outer section of the impeller where the blade is located is R86; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the blade section and the range of the six-segment blade section parameters, the outer section parameters of the impeller hub where the blade is located, and the outer section parameters of the impeller where the blade is located.

[0034] Example 2 Combination Figure 15-Figure 21 As shown, the submersible pump uses axial flow blades and guide vanes. The guide vanes are divided into six sections of guide vane cross-sections in the radial direction of the guide vane hub. The first guide vane section is R104.9, the angle θ is 46.36°, and the projection arc range is -18.4° to 17.88°; the second guide vane section is R94.76, the angle θ is 49.19°, and the projection arc range is -18.39° to 18.04°; the third guide vane section is R84.63, the angle θ is 52.24°, and the projection arc range is -18.38° to 18.25°; the fourth guide vane section is R74.5, the angle θ is 55.58°, and the projection arc range is The radian range is -18.37° to 18.54°; the fifth guide vane blade section is R64.38, the angle θ is 59.18°, and the projected radian range is -18.37° to 18.92°; the sixth guide vane blade section is R54.25, the angle θ is 63.09°, and the projected radian range is -18.38° to 19.42°; the hub outer section of the guide vane is R49, and the outer section of the guide vane is R108.5; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the guide vane section and the range of the six-segment guide vane section parameters, the guide vane hub outer section parameters, and the guide vane outer section parameters.

[0035] Combination Figure 22-Figure 28As shown, the blade is divided into six blade sections in the radial direction of the blade hub. The first blade section is R104.4, the angle is 19.34°, and the projection arc range is -42.69° to 35.81°; the second blade section is R94.32, the angle is 22.2°, and the projection arc range is -43.87° to 37.16°; the third blade section is R84.24, the angle is 25.67°, and the projection arc range is -45.15° to 38.79°; the fourth blade section is R74.16, the angle is 29.88°, and the projection arc range is -46.53°. ° to 40.73°; ​​the fifth blade section is R64.08, the angle is 35.05°, and the projection arc range is -47.87° to 43.03°; the sixth blade section is R54, the angle is 41.34°, and the projection arc range is -48.98° to 45.67°; the hub outer section of the impeller where the blade is located is R49, and the outer section of the impeller where the blade is located is R108; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the blade section and the range of the six-segment blade section parameters, the outer section parameters of the impeller hub where the blade is located, and the outer section parameters of the impeller where the blade is located.

[0036] Example 3 Combination Figure 29-Figure 35 As shown, the submersible pump uses axial flow blades and guide vanes. The guide vanes are divided into six sections of guide vane cross-sections in the radial direction of the guide vane hub. The first guide vane section is R112.62, θ is 64.32°, and the projection arc range is -18.4° to 17.13°; the second guide vane section is R101.74, θ is 60.45°, and the projection arc range is -18.39° to 17.37°; the third guide vane section is R90.87, θ is 56.92°, and the projection arc range is -18.38° to 17.67°; the fourth guide vane section is R80, θ is 53.67°, and the projection arc range is The range is -18.38° to 18.04°; the fifth guide vane section is R69.12, θ is 50.68°, and the projected arc range is -18.38° to 18.48°; the sixth guide vane section is R58.25, θ is 47.93°, and the projected arc range is -18.38° to 19.07°; the hub outer section of the guide vane is R54.5, and the outer section of the guide vane is R116.5; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the guide vane section and the range of the six-segment guide vane section parameters, the guide vane hub outer section parameters, and the guide vane outer section parameters.

[0037] Combination Figure 36-Figure 42As shown in the figure, the blade is divided into six blade sections in the radial direction of the blade hub. The first blade section is R112.13, θ is 22.63°, and the projected arc range is -36.45° to 38.88°; the second blade section is R101.31, the angle is 25.59°, and the projected arc range is -38.08° to 38.48°; the third blade section is R90.48, the angle is 28.9°, and the projected arc range is -39.81° to 38.16°; the fourth blade section is R79.65, the angle is 32.92°, and the projected arc range is -41. 72° to 38.08°; the fifth blade section is R68.83, the angle is 37.52°, and the projection arc range is -43.89° to 38.47°; the sixth blade section is R58, the angle is 42.8°, and the projection arc range is -46.53° to 39.7°; the hub outer section of the impeller where the blade is located is R54, and the outer section of the impeller where the blade is located is R116; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the blade section and the range of the six-segment blade section parameters, the outer section parameters of the impeller hub where the blade is located, and the outer section parameters of the impeller where the blade is located.

[0038] The embodiment of the present application also discloses a submersible pump.

[0039] Embodiment 1 Combination Fig.43 and Fig.44 As shown, the submersible pump includes a pump body 1 and a motor 2 that are assembled and used together. The pump body 1 is equipped with the above-mentioned axial flow blades and guide vanes for the submersible pump, and the output shaft of the motor 2 is coaxially driven and connected with the blades. The motor 2 includes a housing, and a stator and a rotor are installed in the housing. The figure shows the internal structure, and the stator and rotor structure and the location are not directly shown. In the embodiment of the present application, the stator is fixedly installed on the inner wall of the housing, the rotor is coaxially fixedly connected with the output shaft of the motor and is coaxially embedded in the stator as a whole, and multiple groups of magnetic steel grooves are evenly opened along the circumferential direction near the outer circle position of the rotor, and magnetic steel sheets are correspondingly inserted and arranged in the magnetic steel grooves to improve the rotor space utilization rate, thereby achieving the purpose of reducing the height of the magnetic steel sheets. Under the premise of meeting the power design requirements of the motor 2, the space utilization rate is improved to reduce the overall design height of the stator and the rotor, thereby realizing the miniaturization design of the motor 2, and the above-mentioned blade and guide vane structure after shape optimization design is added, so as to achieve the overall miniaturization and weight reduction design purpose of the submersible pump.

[0040] A sealed chamber 21 is formed in the casing of the motor 2. The chamber 21 is used to install the above-mentioned stator and rotor, that is, the stator is fixedly installed on the inner wall of the chamber 21, and lubricating oil is injected into the chamber 21. The lubricating oil soaks the stator and the rotor to play a role in lubrication and cooling. An oil filling hole is also provided on the bottom surface of the casing of the motor 2. A plugging seal is usually installed at the oil filling hole. The plugging seal can be a rubber plug or other plugging piece. When the lubricating oil needs to be replenished, the plugging seal can be removed to inject oil into the chamber 21. It should be noted that the injection height of the lubricating oil in the chamber 21 does not exceed one-third of the chamber height.

[0041] In addition, the position where the chamber 21 is connected to the external cable is realized by the cable oil seal 5. In the embodiment of the present application, the cable oil seal 5 is a disc-shaped copper structure, which is vertically clamped in the housing of the motor 2 and used to connect to the connecting tube shell 22 of the external cable to seal the chamber 21. When wiring, the external cable is electrically connected to the outside of the cable oil seal, and the internal wires of the motor 2 are electrically connected to the inside of the cable oil seal, thereby realizing the power supply connection.

[0042] Specifically, combined Fig.44 and Fig.45 As shown, the connecting tube shell 22 includes an inner tube structure 221 and an outer tube structure 222. The inner tube structure 221 is integrally formed with the casing of the motor 2, while the outer tube structure 222 is processed separately and then plugged, assembled and locked with the inner tube structure 221. The inner tube structure 221 and the outer tube structure 222 are sealed and connected via a sealing ring 223.

[0043] The pump body 1 specifically includes a pump housing 11 and a water inlet section 12. The pump housing 11 is connected to the housing of the motor 2 through the water inlet section 12, and the housing of the motor 2 and the water inlet section 12 are integrated, which improves the structural integrity of the submersible pump, and the pump housing 11 and the water inlet section 12 are detachably connected, thereby achieving the purpose of split assembly. The blade is drivingly connected to the output shaft or pump shaft of the motor 2 and is placed at the water inlet section 12, and the guide vane is fixedly installed at the water outlet of the pump housing 11.

[0044] A hook structure 3 is also formed on the outside of the water inlet node 12, and a mesh cover 4 can be hung on the water inlet node 12 through the hook structure 3. The mesh cover 4 is arranged at the water inlet of the water inlet node 12 to prevent debris in the water from entering the position of the blades and guide vanes through the water inlet node 12.

[0045] The water outlet of the pump body 1 can also be connected to a water outlet pipe, and the water outlet pipe and the water outlet of the pump body 1 are fixed in a detachable connection manner, such as a threaded connection or an adapter clamping connection, so as to achieve the purpose of pumping water outward through the pipe structure.

[0046] Embodiment 2 Reference Fig.46 As shown, the difference between the submersible pump disclosed in the embodiment of the present application and the embodiment 1 is that the installation structure of the cable oil seal 5 is different. In the embodiment of the present application, an elastic compensation structure 1 225 is introduced at the clamping and fixing position of the sealing ring 223, and a sealing gasket 224 and a corresponding elastic compensation structure 2 226 are arranged at the clamping and fixing position of the cable oil seal 5. The sealing gasket 224 is essentially consistent with the material and sealing principle of the sealing ring 223, but it is different in shape due to the different arrangement positions. The structures of the elastic compensation structure 1 225 and the elastic compensation structure 2 226 are completely consistent. The former provides an elastic compensation margin for the sealing ring 223, while the latter provides an elastic compensation margin for the sealing gasket 224.

[0047] Specifically, in the embodiment of the present application, the elastic compensation structure 1 225 and the elastic compensation structure 2 26 both include elastic parts and a base. An annular notch is provided at the end surface of the inner tube structure 221 to fix the base of the elastic compensation structure 1 225 and to allow the sealing ring 223 to slide. The base and the sealing ring 223 are both annular structures, and multiple groups of elastic parts in a compressed state are connected between the two. The elastic parts can be springs, etc.; correspondingly, an annular recess is provided at the inner side surface of the inner tube structure 221 to fix the base of the elastic compensation structure 2 226 and to allow the sealing gasket 224 to slide. The base and the sealing gasket 224 are also annular structures, and multiple groups of elastic parts in a compressed state are connected between the two. The elastic parts can also be springs.

[0048] Taking into account the problems of machining and manufacturing precision, assembly errors and possible wear problems with increasing use time, elastic compensation structure 1 225 and elastic compensation structure 226 are introduced to compensate from the two angles of end face sealing and inner ring face sealing respectively, thereby realizing a secondary sealing structure with better sealing effect and improving the effectiveness of sealing cooperation.

[0049] 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. Axial flow blades and guide vanes for submersible pumps, characterized in that: It comprises blades and guide vanes with shortened lengths, wherein the blades and guide vanes cooperate to form a blade-guide vane group with shortened lengths; the blades are divided into N blade cross sections in the radial direction of the impeller hub, and the stacking line of the blades is determined by a combination of N blade cross sections, an outer cross section of the impeller hub where the blades are located, and a curved surface extension stacking point combination of the outer cross section of the impeller; the guide vanes are divided into N guide vane cross sections in the radial direction of the guide vane hub, and the stacking line of the guide vanes is determined by a combination of N guide vane cross sections, an outer cross section of the guide vane hub, and a curved surface extension stacking point combination of the outer cross section of the guide vane.

2. The axial flow blade and guide vane for a submersible pump according to claim 1, characterized in that: The guide vane is divided into six sections of guide vane cross-sections in the radial direction of the guide vane hub. The first guide vane section is R83.6, the angle 1 is 48.5°, the angle 2 is 36.23°, and the projection arc range is -23.39° to 17.31°; the second guide vane section is R75.54, the angle 1 is 50.61°, the angle 2 is 40.99°, and the projection arc range is -24.15° to 17.35°; the third guide vane section is R67.47, the angle 1 is 52.84°, the angle 2 is 47.03°, and the projection arc range is -25.11° to 17.4°; the fourth guide vane section is R59.4, the angle 1 is 55.6°, the angle 2 is 52.9°, and the projection arc range is The angle range is -26.37° to 17.46°; the fifth guide vane section is R51.32, the angle 1 is 58.81°, the angle 2 is 58.81°, and the projected arc range is -28.09° to 17.56°; the sixth guide vane section is R43.25, the angle 1 is 62.94°, the angle 2 is 62.94°, and the projected arc range is -30.57° to 17.7°; the hub outer section of the guide vane is R35, and the outer section of the guide vane is R86.5; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the guide vane section and the parameters of the six sections of the guide vane section, the hub outer section parameters of the guide vane, and the range of the outer section parameters of the guide vane; The blade is divided into six blade sections in the radial direction of the blade hub. The first blade section is R83.13, the angle is 30.99°, and the projected arc range is -42.67° to 39.27°; the second blade section is R75.1, the angle is 33.61°, and the projected arc range is -43.6° to 39.86°; the third blade section is R67.08, the angle is 36.62°, and the projected arc range is -44.78° to 40.68°; the fourth blade section is R59.05, the angle is 40.31°, and the projected arc range is -46.33° to 41.6 6°; the fifth blade section R51.03, the angle is 44.45°, the projection arc range is -48.45° to 42.97°; the sixth blade section R43, the angle is 49.35°, the projection arc range is -51.54° to 45.31°; the hub outer section of the impeller where the blade is located is R35, and the outer section of the impeller where the blade is located is R86; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the blade section and the parameters of the six blade sections, the hub outer section parameters of the impeller where the blade is located, and the outer section parameters of the impeller where the blade is located.

3. The axial flow blade and guide vane for a submersible pump according to claim 1, characterized in that: The guide vane is divided into six sections in the radial direction of the guide vane hub. The first guide vane section is R104.9, the angle θ is 46.36°, and the projected arc range is -18.4° to 17.88°; the second guide vane section is R94.76, the angle θ is 49.19°, and the projected arc range is -18.39° to 18.04°; the third guide vane section is R84.63, the angle θ is 52.24°, and the projected arc range is -18.38° to 18.25°; the fourth guide vane blade section is R74.5, the angle θ is 55.58°, and the projected arc range is -18.37° to 18.54°; the fifth guide vane blade section is R64.38, the angle θ is 59.18°, and the projected arc range is -18.37° to 18.92°; the sixth guide vane blade section is R54.25, the angle θ is 63.09°, and the projected arc range is -18.38° to 19.42°; the hub outer section of the guide vane is R49, and the outer section of the guide vane is R108.5; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the guide vane section and the parameters of the six sections of the guide vane section, the hub outer section parameters of the guide vane, and the range of the outer section parameters of the guide vane; The blade is divided into six blade sections in the radial direction of the blade hub. The first blade section is R104.4, the angle is 19.34°, and the projected arc range is -42.69° to 35.81°; the second blade section is R94.32, the angle is 22.2°, and the projected arc range is -43.87° to 37.16°; the third blade section is R84.24, the angle is 25.67°, and the projected arc range is -45.15° to 38.79°; the fourth blade section is R74.16, the angle is 29.88°, and the projected arc range is -46.53° to 40.7 3°; the fifth blade section is R64.08, the angle is 35.05°, and the projected arc range is -47.87° to 43.03°; the sixth blade section is R54, the angle is 41.34°, and the projected arc range is -48.98° to 45.67°; the hub outer section of the impeller where the blade is located is R49, and the outer section of the impeller where the blade is located is R108; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the blade section and the parameters of the six blade sections, the hub outer section parameters of the impeller where the blade is located, and the outer section parameters of the impeller where the blade is located.

4. The axial flow blade and guide vane for a submersible pump according to claim 1, characterized in that: The guide vane is divided into six sections of guide vane cross-sections in the radial direction of the guide vane hub. The first guide vane cross-section R112.62, θ is 64.32°, and the projected arc range is -18.4° to 17.13°; the second guide vane cross-section R101.74, θ is 60.45°, and the projected arc range is -18.39° to 17.37°; the third guide vane cross-section R90.87, θ is 56.92°, and the projected arc range is -18.38° to 17.67°; the fourth guide vane cross-section R80, θ is 53.67°, and the projected arc range is -18.38° to 1 8.04°; the fifth guide vane section is R69.12, θ is 50.68°, and the projected arc range is -18.38° to 18.48°; the sixth guide vane section is R58.25, θ is 47.93°, and the projected arc range is -18.38° to 19.07°; the hub outer section of the guide vane is R54.5, and the outer section of the guide vane is R116.5; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the guide vane section and the parameters of the six sections of the guide vane section, the hub outer section parameters of the guide vane, and the range of the outer section parameters of the guide vane; The blade is divided into six blade sections in the radial direction of the blade hub. The first blade section is R112.13, θ is 22.63°, and the projected arc range is -36.45° to 38.88°; the second blade section is R101.31, the angle is 25.59°, and the projected arc range is -38.08° to 38.48°; the third blade section is R90.48, the angle is 28.9°, and the projected arc range is -39.81° to 38.16°; the fourth blade section is R79.65, the angle is 32.92°, and the projected arc range is -41.72° to 38. 08°; the fifth blade section is R68.83, the angle is 37.52°, and the projected arc range is -43.89° to 38.47°; the sixth blade section is R58, the angle is 42.8°, and the projected arc range is -46.53° to 39.7°; the hub outer section of the impeller where the blade is located is R54, and the outer section of the impeller where the blade is located is R116; the guide vane stacking line is determined by the combination of the curved surface extension stacking points of the blade section and the parameters of the six blade sections, the hub outer section parameters of the impeller where the blade is located, and the outer section parameters of the impeller where the blade is located.

5. A submersible pump comprising a pump body (1) and a motor (2), characterized in that: The pump body (1) is provided with axial flow blades and guide vanes for a submersible pump as described in any one of claims 1 to 4 above, the motor (2) is drivingly connected to the blades, the motor (2) comprises a stator and a rotor, and a plurality of groups of magnetic steel grooves are evenly arranged along the circumferential direction near the outer circle of the rotor, and the magnetic steel grooves are provided with magnetic steel sheets.

6. The submersible pump according to claim 5, characterized in that: A sealed chamber (21) is formed in the casing of the motor (2), the chamber (21) is used to install the stator and the rotor, and lubricating oil is injected into the chamber (21).

7. The submersible pump according to claim 6, characterized in that: An oil filling hole is provided on the bottom surface of the casing of the motor (2), and a sealing member is provided on the oil filling hole.

8. The submersible pump according to claim 6 or 7, characterized in that: The injection height of the lubricating oil liquid in the chamber (21) does not exceed one third of the chamber height of the chamber (21).

9. The submersible pump according to claim 5, characterized in that: The pump body (1) comprises a pump casing (11) and a water inlet joint (12); the pump casing (11) is connected to the casing of the motor (2) via the water inlet joint (12); and the casing of the motor (2) and the water inlet joint (12) are arranged in an integrated manner.

10. The submersible pump according to claim 9, characterized in that: The pump casing (11) is detachably connected to the water inlet section (12); the blades are drivingly connected to the pump shaft of the motor (2) and are disposed in the water inlet section (12); and the guide vanes are fixedly disposed at the water outlet of the pump casing (11).

11. The submersible pump according to claim 9, characterized in that: The water inlet section (12) is provided with a hook structure (3), and the water inlet section (12) is hung with a mesh cover (4) via the hook structure (3), and the mesh cover (4) covers the water inlet of the water inlet section (12).

12. The submersible pump according to claim 5, characterized in that: The water outlet of the pump body (1) is connected to a water outlet pipe, and the water outlet pipe is detachably connected to the water outlet of the pump body (1).

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