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

Abstract

The present application relates to the fields of emergency rescue and fire fighting technologies, and discloses an axial flow blade and a guide vane for a submersible pump and the submersible pump. The blade and the guide vane of the axial flow submersible pump cooperate to form a blade-guide vane group; the blade is divided into N blade cross-sections, and the stacking line of the blade is determined by the combination of the N blade cross-sections, the outer cross-section of the hub of the impeller where the blade is located, and the curved surface extension stacking points of the outer cross-section of the impeller; the guide vane is divided into N guide vane cross-sections, and the stacking line of the guide vane is determined by the combination of the N guide vane cross-sections, the outer cross-section of the hub of the guide vane, and the curved surface extension stacking points of the outer cross-section of the guide vane. A blade-guide vane group that is shorter in length than the blades and guide vanes of the original submersible pump is adopted, and the stacking lines of the guide vane and the blade are determined by using the cross-sections of multiple segments of the guide vane and the blade, the outer cross-section of the hub, and the curved surface extension stacking points of the outer cross-section, so as to determine the main shapes of the guide vane and the blade, meet the working requirements of lift and flow rate, and at the same time reduce the overall weight of the submersible pump from the pump body direction and reduce the handling difficulty.

Description

Technical Field

[0001] This application relates to the technical fields of emergency rescue and fire fighting, in particular to axial flow blades, 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 applied in fields such as emergency rescue, fire fighting, agricultural irrigation, and emergency rescue.

[0003] Submersible motor pumps are a combination of a pump body and an electric motor and are widely used in the fields of emergency rescue and fire fighting. The electric motor of the submersible motor pump is sealed, and the whole motor can work in water. The motor drives the impeller at the water inlet of the pump body to rotate. The blades of the impeller rotate to suck liquid from the water inlet of the pump body and push it towards the water outlet of the pump body. The liquid is then pumped outwards after being guided by the guide vane at the water outlet of the pump body.

[0004] When using submersible motor pumps in the fields of emergency rescue and fire fighting, it is often necessary to carry the submersible motor pumps. However, the combined weight of the pump body and the motor of the existing submersible motor pumps is relatively heavy, which is not convenient for users to carry. Frequent carrying will cause excessive fatigue of personnel and even problems such as personnel operation injuries and equipment handling damages. In emergency rescue operations and fire fighting operations, such problems are likely to cause serious consequences. Summary of the Invention

[0005] In order to solve the problem that the combined weight of the pump body and the motor of the existing submersible pump is relatively heavy and not convenient for operators to carry, this application provides axial flow blades, guide vanes for submersible pumps, and submersible pumps.

[0006] In the first aspect, this application provides axial flow blades and guide vanes for submersible pumps, adopting the following technical solutions:

[0007] Axial flow blades and guide vanes for submersible pumps include blades and guide vanes with shortened lengths. The blades and the guide vanes cooperate to form a blade-guide vane group with a shortened length. The blades are divided into N blade cross-sections in the radial direction of the impeller hub. The stacking line of the blades is determined by the combination of N blade cross-sections, the outer cross-section of the hub of the impeller where the blades are located, and the curved surface extension stacking points 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. The stacking line of the guide vanes is determined by the combination of N guide vane cross-sections, the outer cross-section of the hub of the guide vane, and the curved surface extension stacking points of the outer cross-section of the guide vane.

[0008] By adopting the above technical solution, a vane-guide vane group with a length shorter than that of the vanes and guide vanes of the original submersible pump is used. The stacking lines of the guide vanes and vanes are determined by means of the combination of the extended stacking points of the curved surfaces of multiple sections of guide vanes, vane cross-sections, outer cross-sections of the guide vane and vane hubs, and outer cross-sections of the guide vanes and vanes, so as to determine the main shapes of the guide vanes and vanes, thereby meeting the operating requirements of head and flow rate. At the same time, the overall weight of the submersible pump is reduced from the pump body direction, and the handling difficulty is reduced.

[0009] Preferably, the guide vane is divided into six guide vane cross-sections in the radial direction of the guide vane hub. The first guide vane cross-section has a radius R83.6, angle 1 is 48.5°, angle 2 is 36.23°, and the projection radian range is from -23.39° to 17.31°; the second guide vane cross-section has a radius R75.54, angle 1 is 50.61°, angle 2 is 40.99°, and the projection radian range is from -24.15° to 17.35°; the third guide vane cross-section has a radius R67.47, angle 1 is 52.84°, angle 2 is 47.03°, and the projection radian range is from -25.11° to 17.4°; the fourth guide vane cross-section has a radius R59.4, angle 1 is 55.6°, angle 2 is 52.9°, and the projection radian range is from -26.37° to 17.46°; the fifth guide vane cross-section has a radius R51.32, angle 1 is 58.81°, angle 2 is 58.81°, and the projection radian range is from -28.09° to 17.56°; the sixth guide vane cross-section has a radius R43.25, angle 1 is 62.94°, angle 2 is 62.94°, and the projection radian range is from -30.57° to 17.7°; the outer cross-section of the guide vane hub is R35, and the outer cross-section of the guide vane is R86.5; the guide vane stacking line is determined by the combination of the curved surface extended stacking points of the guide vane cross-sections and the ranges of the parameters of the six guide vane cross-sections, the parameters of the outer cross-section of the guide vane hub, and the parameters of the outer cross-section of the guide vane; the blade is divided into six blade cross-sections in the radial direction of the blade hub. The first blade cross-section has a radius R83.13 and an angle of 30.99°, and the projection radian range is from -42.67° to 39.27°; the second blade cross-section has a radius R75.1 and an angle of 33.61°, and the projection radian range is from -43.6° to 39.86°; the third blade cross-section has a radius R67.08 and an angle of 36.62°, and the projection radian range is from -44.78° to 40.68°; the fourth blade cross-section has a radius R59.05 and an angle of 40.31°, and the projection radian range is from -46.33° to 41.66°; the fifth blade cross-section has a radius R51.03 and an angle of 44.45°, and the projection radian range is from -48.45° to 42.97°; the sixth blade cross-section has a radius R43 and an angle of 49.35°, and the projection radian range is from -51.54° to 45.31°; the outer cross-section of the hub of the impeller where the blade is located is R35, and the outer cross-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 extended stacking points of the blade cross-sections and the ranges of the parameters of the six blade cross-sections, the parameters of the outer cross-section of the hub of the impeller where the blade is located, and the parameters of the outer cross-section of the impeller where the blade is located.

[0010] Preferably, the guide vane is divided into six guide vane cross-sections in the radial direction of the guide vane hub. The first guide vane cross-section has a radius R104.9, an angle θ of 46.36°, and a projection radian range from -18.4° to 17.88°; the second guide vane cross-section has a radius R94.76, an angle θ of 49.19°, and a projection radian range from -18.39° to 18.04°; the third guide vane cross-section has a radius R84.63, an angle θ of 52.24°, and a projection radian range from -18.38° to 18.25°; the fourth guide vane blade cross-section has a radius R74.5, an angle θ of 55.58°, and a projection radian range from -18.37° to 18.54°; the fifth guide vane blade cross-section has a radius R64.38, an angle θ of 59.18°, and a projection radian range from -18.37° to 18.92°; the sixth guide vane blade cross-section has a radius R54.25, an angle θ of 63.09°, and a projection radian range from -18.38° to 19.42°; the outer cross-section of the guide vane hub is R49, and the outer cross-section of the guide vane is R108.5; the guide vane stacking line is determined by the combination of the curved surface extended stacking points of the guide vane cross-sections and the ranges of the parameters of the six guide vane cross-sections, the parameters of the outer cross-section of the guide vane hub, and the parameters of the outer cross-section of the guide vane; the blade is divided into six blade cross-sections in the radial direction of the blade hub. The first blade cross-section has a radius R104.4, an angle of 19.34°, and a projection radian range from -42.69° to 35.81°; the second blade cross-section has a radius R94.32, an angle of 22.2°, and a projection radian range from -43.87° to 37.16°; the third blade cross-section has a radius R84.24, an angle of 25.67°, and a projection radian range from -45.15° to 38.79°; the fourth blade cross-section has a radius R74.16, an angle of 29.88°, and a projection radian range from -46.53° to 40.73°; the fifth blade cross-section has a radius R64.08, an angle of 35.05°, and a projection radian range from -47.87° to 43.03°; the sixth blade cross-section has a radius R54, an angle of 41.34°, and a projection radian range from -48.98° to 45.67°; the outer cross-section of the hub of the impeller where the blade is located is R49, and the outer cross-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 extended stacking points of the blade cross-sections and the ranges of the parameters of the six blade cross-sections, the parameters of the outer cross-section of the hub of the impeller where the blade is located, and the parameters of the outer cross-section of the impeller where the blade is located.

[0011] Preferably, the guide vane is divided into six guide vane cross-sections in the radial direction of the guide vane hub. For the first guide vane cross-section, R is 112.62 and θ is 64.32°, and the projected radian range is from -18.4° to 17.13°; for the second guide vane cross-section, R is 101.74 and θ is 60.45°, and the projected radian range is from -18.39° to 17.37°; for the third guide vane cross-section, R is 90.87 and θ is 56.92°, and the projected radian range is from -18.38° to 17.67°; for the fourth guide vane cross-section, R is 80 and θ is 53.67°, and the projected radian range is from -18.38° to 18.04°; for the fifth guide vane cross-section, R is 69.12 and θ is 50.68°, and the projected radian range is from -18.38° to 18.48°; for the sixth guide vane cross-section, R is 58.25 and θ is 47.93°, and the projected radian range is from -18.38° to 19.07°. The outer cross-section of the guide vane hub is R54.5, and the outer cross-section of the guide vane is R116.5. The guide vane stack line is determined by the combination of the curved surface extended stacking points of the guide vane cross-sections and the parameter ranges of the six guide vane cross-sections, the outer cross-section parameter of the guide vane hub, and the outer cross-section parameter of the guide vane. The blade is divided into six blade cross-sections in the radial direction of the blade hub. For the first blade cross-section, R is 112.13 and θ is 22.63°, and the projected radian range is from -36.45° to 38.88°; for the second blade cross-section, R is 101.31 and the angle is 25.59°, and the projected radian range is from -38.08° to 38.48°; for the third blade cross-section, R is 90.48 and the angle is 28.9°, and the projected radian range is from -39.81° to 38.16°; for the fourth blade cross-section, R is 79.65 and the angle is 32.92°, and the projected radian range is from -41.72° to 38.08°; for the fifth blade cross-section, R is 68.83 and the angle is 37.52°, and the projected radian range is from -43.89° to 38.47°; for the sixth blade cross-section, R is 58 and the angle is 42.8°, and the projected radian range is from -46.53° to 39.7°. The outer cross-section of the hub of the impeller where the blade is located is R54, and the outer cross-section of the impeller where the blade is located is R116. The guide vane stack line is determined by the combination of the curved surface extended stacking points of the blade cross-sections and the parameter ranges of the six blade cross-sections, the outer cross-section parameter of the hub of the impeller where the blade is located, and the outer cross-section parameter of the impeller where the blade is located.

[0012] In a second aspect, the present application provides a submersible pump, adopting the following technical solutions:

[0013] The submersible pump includes a pump body and a motor. The pump body is provided with the axial flow blades and guide vanes for the submersible pump. The motor is drivingly connected to the blades. The motor includes a stator and a rotor. A plurality of magnet steel grooves are evenly opened in the circumferential direction at a position close to the outer circle of the rotor, and magnet steel sheets are arranged in the magnet steel grooves.

[0014] By adopting the above technical solution, the arrangement position and quantity of the magnetic steel grooves at the rotor are optimized, that is, the arrangement position and quantity of the magnetic steel sheets are optimized, the space utilization rate of the rotor is improved, and the arrangement quantity of the magnetic steel sheets is increased. Therefore, the arrangement quantity of the magnetic steel sheets can be increased while reducing the length of the magnetic steel sheets, still meeting the working requirements of the motor of the submersible pump, and further achieving the purpose of jointly reducing the overall weight of the submersible pump from two directions of the pump body and the motor, which is convenient for the user to carry.

[0015] Preferably, a sealed chamber is formed in the housing of the motor, the chamber is used for installing the stator and the rotor, and a lubricating oil liquid is injected into the chamber.

[0016] By adopting the above technical solution, the lubricating oil liquid can not only play a lubricating role, but also play a role in cooling and temperature reduction. Especially in the working condition environment where the submersible pump needs to be started and stopped frequently, it has a good heat dissipation effect.

[0017] Preferably, an oil injection hole is opened on the bottom surface of the housing of the motor, and a plugging seal is arranged on the oil injection hole.

[0018] By adopting the above technical solution, the lubricating oil liquid can be supplemented into the chamber through the oil injection hole on the bottom surface of the motor housing, which has good operability.

[0019] Preferably, the injection height of the lubricating oil liquid in the chamber does not exceed one-third of the chamber height.

[0020] By adopting the above technical solution, the filling amount of the lubricating oil liquid in the chamber is limited to avoid affecting the normal operation of the motor stator and rotor, and at the same time, a good heat dissipation effect can still be obtained.

[0021] Preferably, the pump body includes a pump housing and a water inlet section, the pump housing is connected to the housing of the motor through the water inlet section, and the housing of the motor and the water inlet section are integrally arranged.

[0022] By adopting the above technical solution, the housing of the motor and the water inlet section are integrally processed and manufactured, which is beneficial to improving the structural strength and stability of the connection between the pump body and the motor and is convenient for handling.

[0023] Preferably, the pump housing is detachably connected to the water inlet section, the impeller is drivingly connected to the pump shaft of the motor and is placed in the water inlet section, and the guide vane is fixedly arranged at the water outlet of the pump housing.

[0024] By adopting the above technical solution, on the basis of the integral connection between the water inlet section and the housing of the motor, the overall disassembly and installation of the guide vane and the pump housing are further realized, and the impeller can be separately disassembled and installed, and then the combined installation and disassembly of the impeller and the guide vane are realized.

[0025] Preferably, the water inlet section is provided with a hook structure, and a net cover is hung on the water inlet section through the hook structure, and the net cover covers the water inlet of the water inlet section.

[0026] By adopting the above technical solution, the net cover can block sundries in the water from entering the pump body, ensuring the normal operation of the submersible pump. At the same time, the hook structure is used to connect the net cover and the water inlet section, which has good operability.

[0027] Preferably, the water outlet of the pump body is connected with a water outlet pipe, and the water outlet pipe is detachably connected to the water outlet of the pump body.

[0028] By adopting the above technical solution, the water outlet pipe is detachably connected to the pump body, which is convenient for quick disassembly, assembly and replacement during operation, and has good practicability.

[0029] In summary, the present application includes at least one of the following beneficial technical effects:

[0030] 1. Using a shorter blade-guide vane group to replace the blades and guide vanes of the original submersible pump, and using the combined determination of the sectional curves of multiple guide vanes and blades, the outer section of the hub, and the outer section to determine the stacking lines of the guide vanes and blades, thereby determining the main shapes of the guide vanes and blades, and meeting the operation requirements of head and flow rate. At the same time, the overall weight of the submersible pump is reduced, and the handling difficulty is reduced;

[0031] 2. Making full use of the available space of the rotor, increasing the number of magnetic steel sheets arranged on the rotor. Under the condition of reducing the length of the magnetic steel sheets, increasing the number of arranged magnetic steel sheets can still meet the motor working requirements of the submersible pump, and thus achieve the purpose of reducing the overall weight of the submersible pump, which is convenient for operators to carry;

[0032] 3. Optimizing the connection structure between the pump body and the motor of the submersible pump, realizing the integrated connection of the motor and the water inlet section of the pump body, and at the same time meeting the requirements of the fitting and combined installation of the pump body blades and guide vanes;

[0033] 4. Injecting lubricating oil into the chamber of the motor where the stator and rotor are located, improving the cooling and heat dissipation effect of the submersible pump, and at the same time enabling oil replenishment operation. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] Figure 1 is a schematic diagram of the sectional parameters of the guide vane in the first embodiment;

[0035] Figure 2 is a schematic diagram of the angle and radian parameters of the first guide vane in the first embodiment;

[0036] Figure 3 is a schematic diagram of the angle and radian parameters of the second guide vane in the first embodiment;

[0037] Figure 4It is a schematic diagram of the angle and radian parameters of the third guide vane in the first embodiment;

[0038] Figure 5 It is a schematic diagram of the angle and radian parameters of the fourth guide vane in the first embodiment;

[0039] Figure 6 It is a schematic diagram of the angle and radian parameters of the fifth guide vane in the first embodiment;

[0040] Figure 7 It is a schematic diagram of the angle and radian parameters of the sixth guide vane in the first embodiment;

[0041] Figure 8 It is a schematic diagram of the cross-sectional parameters of each blade in the first embodiment;

[0042] Figure 9 It is a schematic diagram of the angle and radian parameters of the first blade in the first embodiment;

[0043] Figure 10 It is a schematic diagram of the angle and radian parameters of the second blade in the first embodiment;

[0044] Figure 11 It is a schematic diagram of the angle and radian parameters of the third blade in the first embodiment;

[0045] Figure 12 It is a schematic diagram of the angle and radian parameters of the fourth blade in the first embodiment;

[0046] Figure 13 It is a schematic diagram of the angle and radian parameters of the fifth blade in the first embodiment;

[0047] Figure 14 It is a schematic diagram of the angle and radian parameters of the sixth blade in the first embodiment;

[0048] Figure 15 It is a schematic diagram of the cross-sectional parameters of each guide vane in the second embodiment;

[0049] Figure 16 It is a schematic diagram of the angle and radian parameters of the first guide vane in the second embodiment;

[0050] Figure 17 It is a schematic diagram of the angle and radian parameters of the second guide vane in the second embodiment;

[0051] Figure 18 It is a schematic diagram of the angle and radian parameters of the third guide vane in the second embodiment;

[0052] Figure 19 It is a schematic diagram of the angle and radian parameters of the fourth guide vane in the second embodiment;

[0053] Figure 20Schematic diagram of the angle and radian parameters of the fifth guide vane in Embodiment 2;

[0054] Figure 21 Schematic diagram of the angle and radian parameters of the sixth guide vane in Embodiment 2;

[0055] Figure 22 Schematic diagram of the cross-section parameters of each blade in Embodiment 2;

[0056] Figure 23 Schematic diagram of the angle and radian parameters of the first blade in Embodiment 2;

[0057] Figure 24 Schematic diagram of the angle and radian parameters of the second blade in Embodiment 2;

[0058] Figure 25 Schematic diagram of the angle and radian parameters of the third blade in Embodiment 2;

[0059] Figure 26 Schematic diagram of the angle and radian parameters of the fourth blade in Embodiment 2;

[0060] Figure 27 Schematic diagram of the angle and radian parameters of the fifth blade in Embodiment 2;

[0061] Figure 28 Schematic diagram of the angle and radian parameters of the sixth blade in Embodiment 2;

[0062] Figure 29 Schematic diagram of the cross-section parameters of each guide vane in Embodiment 3;

[0063] Figure 30 Schematic diagram of the angle and radian parameters of the first guide vane in Embodiment 3;

[0064] Figure 31 Schematic diagram of the angle and radian parameters of the second guide vane in Embodiment 3;

[0065] Figure 32 Schematic diagram of the angle and radian parameters of the third guide vane in Embodiment 3;

[0066] Figure 33 Schematic diagram of the angle and radian parameters of the fourth guide vane in Embodiment 3;

[0067] Figure 34 Schematic diagram of the angle and radian parameters of the fifth guide vane in Embodiment 3;

[0068] Figure 35 Schematic diagram of the angle and radian parameters of the sixth guide vane in Embodiment 3;

[0069] Figure 36 Schematic diagram of the cross-section parameters of each blade in Embodiment 3;

[0070] Figure 37 It is a schematic diagram of the angle and radian parameters of the first blade in Embodiment 3;

[0071] Figure 38 It is a schematic diagram of the angle and radian parameters of the second blade in Embodiment 3;

[0072] Figure 39 It is a schematic diagram of the angle and radian parameters of the third blade in Embodiment 3;

[0073] Figure 40 It is a schematic diagram of the angle and radian parameters of the fourth blade in Embodiment 3;

[0074] Figure 41 It is a schematic diagram of the angle and radian parameters of the fifth blade in Embodiment 3;

[0075] Figure 42 It is a schematic diagram of the angle and radian parameters of the sixth blade in Embodiment 3;

[0076] Figure 43 It is a schematic diagram of the overall structure of the submersible pump in the implementation of this application;

[0077] Figure 44 It is a schematic diagram of the sectional structure of the submersible pump in the embodiment of this application;

[0078] Figure 45 It is Figure 44 an enlarged schematic diagram of part A in;

[0079] Figure 46 It is a schematic diagram of the installation structure of the cable oil seal in Embodiment 2 of this application.

[0080] Explanation of reference numerals: 1, pump body; 11, pump casing; 12, inlet section; 2, motor; 21, chamber; 22, connecting pipe casing; 221, inner pipe structure; 222, outer pipe structure; 223, sealing ring; 224, sealing gasket; 225, first elastic compensation structure; 226, second elastic compensation structure; 3, hook structure; 4, mesh cover; 5, cable oil seal. Detailed implementation manners

[0081] The following further elaborates on this application in conjunction with the attached Figures 1 - 46 drawings.

[0082] The embodiments of this application disclose axial flow blades and guide vanes for submersible pumps.

[0083] Embodiment 1

[0084] Axial flow blades and guide vanes for submersible pumps, including blades and guide vanes with shortened lengths, the blades and the guide vanes cooperate to form a blade-guide vane group with a shortened length; 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 the combination of N blade cross-sections, the outer cross-section of the hub of the impeller where the blades are located, and the curved surface extension stacking points 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 the combination of N guide vane cross-sections, the outer cross-section of the hub of the guide vanes, and the curved surface extension stacking points of the outer cross-section of the guide vanes.

[0085] Combined with Figures 1 - 7 As shown, the guide vane angles on the six guide vane cross-sections are θ, and the change of the angle θ of the guide vane cross-section rotates around the rotation center point of span=(5.58, -7.43). The guide vane blade cross-section is defined by the radius where it is located. The guide vanes are divided into six guide vane cross-sections in the radial direction of the guide vane hub. The first guide vane cross-section is R83.6, angle 1 is 48.5°, angle 2 is 36.23°, and the projection radian range is from -23.39° to 17.31°; the second guide vane cross-section is R75.54, angle 1 is 50.61°, angle 2 is 40.99°, and the projection radian range is from -24.15° to 17.35°; the third guide vane cross-section is R67.47, angle 1 is 52.84°, angle 2 is 47.03°, and the projection radian range is from -25.11° to 17.4°; the fourth guide vane cross-section is R59.4, angle 1 is 55.6°, angle 2 is 52.9°, and the projection radian range is from -26.37° to 17.46°; the fifth guide vane cross-section is R51.32, angle 1 is 58.81°, angle 2 is 58.81°, and the projection radian range is from -28.09° to 17.56°; the sixth guide vane cross-section is R43.25, angle 1 is 62.94°, angle 2 is 62.94°, and the projection radian range is from -30.57° to 17.7°; the outer cross-section of the hub of the guide vanes is R35, and the outer cross-section of the guide vanes is R86.5; the stacking line of the guide vanes is determined by the combination of the curved surface extension stacking points of the guide vane cross-sections and the ranges of the parameters of the six guide vane cross-sections, the parameters of the outer cross-section of the hub of the guide vanes, and the parameters of the outer cross-section of the guide vanes.

[0086] Combined with Figures 8 - 14As shown, the blade is divided into six blade sections in the radial direction of the blade hub radius. The blade angles of the six blade sections are θ. The change of the blade section angle θ rotates around the rotation center point of span=(2.95, -9.29). The blade section is defined by the radius where it is located. The first blade section is R83.13, with an angle of 30.99°, and the projection radian range is from -42.67° to 39.27°; the second blade section is R75.1, with an angle of 33.61°, and the projection radian range is from -43.6° to 39.86°; the third blade section is R67.08, with an angle of 36.62°, and the projection radian range is from -44.78° to 40.68°; the fourth blade section is R59.05, with an angle of 40.31°, and the projection radian range is from -46.33° to 41.66°; the fifth blade section is R51.03, with an angle of 44.45°, and the projection radian range is from -48.45° to 42.97°; the sixth blade section is R43, with an angle of 49.35°, and the projection radian range is from -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 extended stacking points of the blade section and the ranges of the six blade section parameters, the outer section parameter of the blade hub where the blade is located, and the outer section parameter of the impeller where the blade is located.

[0087] Embodiment 2

[0088] Combined with Figures 15 - 21 As shown, the axial flow blade and the guide vane for a submersible pump. The guide vane is divided into six guide vane sections in the radial direction of the guide vane hub radius. The first guide vane section is R104.9, with an angle θ of 46.36°, and the projection radian range is from -18.4° to 17.88°; the second guide vane section is R94.76, with an angle θ of 49.19°, and the projection radian range is from -18.39° to 18.04°; the third guide vane section is R84.63, with an angle θ of 52.24°, and the projection radian range is from -18.38° to 18.25°; the fourth guide vane blade section is R74.5, with an angle θ of 55.58°, and the projection radian range is from -18.37° to 18.54°; the fifth guide vane blade section is R64.38, with an angle θ of 59.18°, and the projection radian range is from -18.37° to 18.92°; the sixth guide vane blade section is R54.25, with an angle θ of 63.09°, and the projection radian range is from -18.38° to 19.42°; the outer section of the hub 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 extended stacking points of the guide vane section and the ranges of the six guide vane section parameters, the outer section parameter of the guide vane hub, and the outer section parameter of the guide vane.

[0089] Combined with Figures 22 - 28As shown in the figure, the blade is divided into six blade cross-sections in the radial direction of the blade hub radius. The first blade cross-section has a radius of R104.4 and an angle of 19.34°, and the projection radian range is from -42.69° to 35.81°; the second blade cross-section has a radius of R94.32 and an angle of 22.2°, and the projection radian range is from -43.87° to 37.16°; the third blade cross-section has a radius of R84.24 and an angle of 25.67°, and the projection radian range is from -45.15° to 38.79°; the fourth blade cross-section has a radius of R74.16 and an angle of 29.88°, and the projection radian range is from -46.53° to 40.73°; the fifth blade cross-section has a radius of R64.08 and an angle of 35.05°, and the projection radian range is from -47.87° to 43.03°; the sixth blade cross-section has a radius of R54 and an angle of 41.34°, and the projection radian range is from -48.98° to 45.67°; the outer cross-section of the hub of the impeller where the blade is located is R49, and the outer cross-section of the impeller where the blade is located is R108; the stacking line of the guide vane is determined by the combination of the curved surface extended stacking points of the blade cross-section and the ranges of the parameters of the six blade cross-sections, the parameters of the outer cross-section of the blade hub, and the parameters of the outer cross-section of the blade.

[0090] Embodiment 3

[0091] Combined with Figures 29 - 35 As shown in the figure, the axial-flow blade and the guide vane for a submersible pump. The guide vane is divided into six guide vane cross-sections in the radial direction of the guide vane hub radius. The first guide vane cross-section has a radius of R112.62 and a θ of 64.32°, and the projection radian range is from -18.4° to 17.13°; the second guide vane cross-section has a radius of R101.74 and a θ of 60.45°, and the projection radian range is from -18.39° to 17.37°; the third guide vane cross-section has a radius of R90.87 and a θ of 56.92°, and the projection radian range is from -18.38° to 17.67°; the fourth guide vane cross-section has a radius of R80 and a θ of 53.67°, and the projection radian range is from -18.38° to 18.04°; the fifth guide vane cross-section has a radius of R69.12 and a θ of 50.68°, and the projection radian range is from -18.38° to 18.48°; the sixth guide vane cross-section has a radius of R58.25 and a θ of 47.93°, and the projection radian range is from -18.38° to 19.07°; the outer cross-section of the hub of the guide vane is R54.5, and the outer cross-section of the guide vane is R116.5; the stacking line of the guide vane is determined by the combination of the curved surface extended stacking points of the guide vane cross-section and the ranges of the parameters of the six guide vane cross-sections, the parameters of the outer cross-section of the guide vane hub, and the parameters of the outer cross-section of the guide vane.

[0092] Combined with Figures 36 - 42As shown, the blade is divided into six blade cross-sections in the radial direction of the blade hub radius. The first blade cross-section has R112.13 and θ of 22.63°, and the projection radian range is from -36.45° to 38.88°; the second blade cross-section has R101.31 and an angle of 25.59°, and the projection radian range is from -38.08° to 38.48°; the third blade cross-section has R90.48 and an angle of 28.9°, and the projection radian range is from -39.81° to 38.16°; the fourth blade cross-section has R79.65 and an angle of 32.92°, and the projection radian range is from -41.72° to 38.08°; the fifth blade cross-section has R68.83 and an angle of 37.52°, and the projection radian range is from -43.89° to 38.47°; the sixth blade cross-section has R58 and an angle of 42.8°, and the projection radian range is from -46.53° to 39.7°; the outer cross-section of the hub of the impeller where the blade is located is R54, and the outer cross-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 extended stacking points of the blade cross-section and the ranges of the six blade cross-section parameters, the outer cross-section parameter of the blade hub of the impeller where the blade is located, and the outer cross-section parameter of the impeller where the blade is located.

[0093] The embodiment of the present application also discloses a submersible pump.

[0094] Embodiment 1

[0095] Combined with Figure 43 and Figure 44 As shown, the submersible pump includes a pump body 1 and a motor 2 that are assembled and used in cooperation. The above-mentioned axial-flow blade and guide vane for the submersible pump are installed in the pump body 1, and the output shaft of the motor 2 is coaxially drivingly connected to the blade. The motor 2 includes a housing, and a stator and a rotor are installed in the housing. In the figure, for the purpose of showing the internal structure, the stator and rotor structures and their positions 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 to the output shaft of the motor and is integrally coaxially embedded in the stator, and a plurality of groups of magnetic steel grooves are evenly opened in the circumferential direction at the position close to the outer circle of the rotor, and magnetic steel sheets are correspondingly inserted in the magnetic steel grooves to improve the space utilization rate of the rotor, so as to achieve the purpose of reducing the height of the magnetic steel sheets. On 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, so as to realize the miniaturized design of the motor 2. Coupled with the above-mentioned blade and guide vane structures after shape optimization design, the overall miniaturization and weight reduction design purposes of the submersible pump are further realized.

[0096] A chamber 21 is formed inside the housing of the motor 2 and is hermetically sealed. 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 a lubricating oil liquid is injected into the chamber 21. The lubricating oil liquid wets the stator and rotor, playing the roles of lubrication and cooling. An oil injection hole is also opened on the bottom surface of the housing of the motor 2. A plugging and sealing member is usually installed at the oil injection hole. The plugging and sealing member can be a plugging member such as a rubber plug. When it is necessary to replenish the lubricating oil liquid, the plugging and sealing member can be removed to inject oil into the chamber 21. It should be noted that the injection height of the lubricating oil liquid in the chamber 21 does not exceed one-third of the height of the chamber.

[0097] In addition, at the position where the chamber 21 is connected to the external cable, it is achieved through the cable oil seal 5. In the embodiment of the present application, the cable oil seal 5 is a disc-shaped copper structural member, which is vertically clamped as a whole in the connecting pipe shell 22 of the housing of the motor 2 for connecting to 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 wire of the motor 2 is electrically connected to the inside of the cable oil seal, thereby achieving the power supply connection.

[0098] Specifically, as shown in Figure 44 and Figure 45 the connecting pipe shell 22 includes an inner pipe structure 221 and an outer pipe structure 222. The inner pipe structure 221 is integrally formed with the housing of the motor 2, while the outer pipe structure 222 is separately processed and then inserted and assembled with the inner pipe structure 221 and locked. Moreover, the inner pipe structure 221 and the outer pipe structure 222 are hermetically connected through a sealing ring 223.

[0099] 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 integrally arranged, improving the structural integrity of the submersible pump. The pump housing 11 and the water inlet section 12 are detachably connected, thereby achieving the purpose of split assembly. The impeller 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.

[0100] A hook structure 3 is also formed on the outside of the water inlet section 12. The water inlet section 12 can be hung with a mesh cover 4 through the hook structure 3. The mesh cover 4 covers the water inlet of the water inlet section 12 to block sundries in the water from entering the positions where the impeller and the guide vane are located through the water inlet section 12.

[0101] 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 threaded connection or adapter clamping, etc., to achieve the purpose of pumping water out through the pipe structure.

[0102] Embodiment Two

[0103] Reference Figure 46 As shown, the difference between the submersible pump disclosed in the embodiment of the present application and that of the first embodiment lies in the different installation structures of the cable oil seal 5. In the embodiment of the present application, an elastic compensation structure 225 is introduced at the clamping and fixing position of the sealing ring 223, and at the same time, a gasket 224 and a corresponding elastic compensation structure 226 are arranged at the clamping and fixing position of the cable oil seal 5. Substantially, the gasket 224 is the same as the sealing ring 223 in terms of material and sealing principle, but only different in shape due to different arrangement positions. The elastic compensation structure 225 and the elastic compensation structure 226 have exactly the same structure. The former provides an elastic compensation margin for the sealing ring 223, while the latter provides an elastic compensation margin for the gasket 224.

[0104] Specifically, in the embodiment of the present application, both the elastic compensation structure 225 and the elastic compensation structure 226 include an elastic member and a base. A circular notch is opened at the end face position of the inner tube structure 221 for fixing the base of the elastic compensation structure 225 and for the sealing ring 223 to slide. Both the base and the sealing ring 223 are circular structures, and a plurality of elastic members in a compressed state are connected between them. The elastic members can be springs, etc. Correspondingly, a circular depression is opened on the inner side surface of the inner tube structure 221 for fixing the base of the elastic compensation structure 226 and for the gasket 224 to slide. Both the base and the gasket 224 are also circular structures, and a plurality of elastic members in a compressed state are also connected between them. The elastic members can also be springs.

[0105] Considering the problems of machining accuracy, assembly error, and possible wear with the increase of service time, the elastic compensation structure 225 and the elastic compensation structure 226 are introduced to compensate from the two aspects of end face sealing and inner ring face sealing respectively, which not only realizes a two-stage sealing structure with better sealing effect, but also improves the effectiveness of the sealing fit.

[0106] The above are all the preferred embodiments of the present application, and the protection scope of the present application is not limited accordingly. Therefore, all equivalent changes made according to the structure, shape, and principle of the present application should be covered within the protection scope of the present application.

Claims

1. 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, the motor (2) is drivingly connected to the blades, the motor (2) comprises a stator and a rotor, a plurality of groups of magnetic steel slots are evenly arranged along the circumferential direction at positions close to the outer circle of the rotor, and the magnetic steel slots are provided with magnetic steel sheets; 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); The chamber (21) is connected to an external cable by a cable oil seal (5), and the cable oil seal (5) is clamped in a connecting tube shell (22) of the housing of the motor (2) and used for connecting to an external cable, so as to seal the chamber (21); The connecting tube shell (22) comprises an inner tube structure (221) and an outer tube structure (222); the inner tube structure (221) is integrally formed with the housing of the motor (2); the outer tube structure (222) is processed separately and then plugged, assembled and locked with the inner tube structure (221); and the inner tube structure (221) and the outer tube structure (222) are sealed with a sealing ring (223); 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 an elastic compensation structure 2 (226) are arranged at the clamping and fixing position of the cable oil seal (5); the elastic compensation structure 1 (225) provides an elastic compensation margin for the sealing ring (223), and the elastic compensation structure 2 (226) provides an elastic compensation margin for the sealing gasket (224).

2. The submersible pump according to claim 1, 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.

3. The submersible pump according to claim 1, 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).

4. The submersible pump according to claim 1, 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.

5. The submersible pump according to claim 4, 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).

6. The submersible pump according to claim 4, 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).

7. The submersible pump according to claim 1, 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).

8. A submersible pump axial flow blade and guide vane for a submersible pump according to any one of claims 1 to 7, 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.

9. The axial flow blade and guide vane for a submersible pump according to claim 8, 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 radian range is -26.37° to 17.46°; the fifth guide vane cross section is R51.32, angle 1 is 58.81°, angle 2 is 58.81°, and the projected radian range is -28.09° to 17.56°; the sixth guide vane cross section is R43.25, angle 1 is 62.94°, angle 2 is 62.94°, and the projected radian range is -30.57° to 17.7°; the hub outer cross section of the guide vane is R35, and the outer cross 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 cross section and the ranges of the six-segment guide vane cross section parameters, the guide vane hub outer cross section parameters, and the guide vane outer cross section parameters; 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. 66°; the fifth 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 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 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.

10. The axial flow blade and guide vane for a submersible pump according to claim 8, 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 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 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 range of the six-segment guide vane section parameters, the guide vane hub outer section parameters, and the guide vane outer section parameters; 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 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.

11. The axial flow blade and guide vane for a submersible pump according to claim 8, 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 18.04°; the fifth guide vane section R69.12, θ is 50.68°, and the projected arc range is -18.38° to 18.48°; the sixth guide vane section 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 ranges of the six-segment guide vane section parameters, the guide vane hub outer section parameters, and the guide vane outer section parameters; 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 3 8.08°; the fifth blade section R68.83, the angle is 37.52°, the projection arc range is -43.89° to 38.47°; the sixth blade section R58, the angle is 42.8°, 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.

Images