Centrifugal water power fan

Abstract

The application relates to a centrifugal water power fan, which comprises a pump body provided with a first cavity, the first cavity is provided with an axial first opening, the cavity wall of the first cavity is provided with a water inlet and a water outlet, a pump cover is used for plugging the first opening, a water power impeller is rotatably arranged in the first cavity, a pump shaft is connected with the water power impeller, and a wind power impeller is connected with the pump shaft; the water power impeller comprises a front cover plate and a rear cover plate, the center of the front cover plate is provided with a water power impeller outlet, a plurality of first water power blades are arranged between the front cover plate and the rear cover plate, a water power impeller inlet is formed between the front cover plate and the rear cover plate, and a pressure relief hole is arranged on the rear cover plate and used for balancing the pressure on both sides of the rear cover plate. The centrifugal water power fan has the following advantages: the design of the pressure relief hole enables water flow to pass through the pressure relief hole from one side of the rear cover plate to the other side of the rear cover plate, the pressure balance on both sides of the rear cover plate is ensured, the rotating resistance of the water power impeller is reduced, and the working efficiency is ensured.

Description

Technical Field

[0001] This invention relates to the field of hydraulic application technology, and in particular to a centrifugal hydraulic fan. Background Technology

[0002] In the existing technology, when a centrifugal hydraulic fan is working, the water flow drives the hydraulic impeller to rotate, which in turn drives the wind turbine blades to rotate. However, the water flow will press the hydraulic impeller inward, resulting in an imbalance of pressure on both sides of the hydraulic impeller. This increases the rotational resistance of the hydraulic impeller and reduces its working efficiency. Summary of the Invention

[0003] One objective of this application is to provide a centrifugal hydraulic fan that can maintain the working efficiency of the hydraulic impeller.

[0004] The technical solution adopted in this application is: a centrifugal hydraulic fan, comprising:

[0005] The pump body has a first cavity with a circular cross-section, the first cavity has a first axial opening, and the cavity wall of the first cavity has an inlet and an outlet.

[0006] Pump cover, used to seal the first opening, and detachably connected to the pump body;

[0007] A hydraulic impeller is rotatably mounted in the first cavity and arranged coaxially with the first cavity;

[0008] The pump shaft is connected to the hydraulic impeller;

[0009] The wind turbine impeller is connected to the pump shaft;

[0010] The pump cover has a second axial opening through which the pump shaft passes. The hydraulic impeller includes a front cover plate and a rear cover plate. The center of the front cover plate has a hydraulic impeller outlet, which is connected to the water outlet. A plurality of first hydraulic blades are provided between the front cover plate and the rear cover plate. A hydraulic impeller inlet is formed between the front cover plate and the rear cover plate, which is connected to the water inlet. A pressure relief hole is provided on the rear cover plate to balance the pressure on both sides of the rear cover plate.

[0011] Compared with the prior art, the advantage of this application lies in the design of the pressure relief hole, which allows water to flow from one side of the rear cover plate through the pressure relief hole to the other side of the rear cover plate, ensuring that the pressure on both sides of the rear cover plate remains balanced, reducing the rotational resistance of the hydraulic impeller, and ensuring working efficiency.

[0012] In some embodiments of this application, the first cavity is provided with a water guide groove, which is arranged around the cavity wall of the first cavity. The top opening of the water guide groove is connected to the first cavity. The width of the top opening of the water guide groove is the same as the width of the hydraulic impeller inlet. The water inlet is connected to the water guide groove. The cross-sectional area of ​​the water guide groove gradually decreases from the outside to the inside. The cross-sectional area of ​​the water guide groove gradually decreases along the circumference of the first cavity, and the cross-sectional area at the connection between the water guide groove and the water inlet is the largest.

[0013] Furthermore, the water inlet direction is tangent to the bottom of the water guide channel; the water inlet is located above the center of the hydraulic impeller; the highest point of the hydraulic impeller inlet is higher than the lowest point of the water inlet.

[0014] In some embodiments of this application, the first hydraulic blade is arranged perpendicularly to the front cover plate, and the first hydraulic blade extends from the outermost side of the front cover plate or the outermost side of the rear cover plate toward the center; the plurality of first hydraulic blades are arranged in a vortex shape toward the outlet of the hydraulic impeller.

[0015] In some embodiments of this application, a second hydraulic blade is provided between adjacent first hydraulic blades, the second hydraulic blade extending from the outermost side of the front cover plate or the outermost side of the rear cover plate toward the center; the second hydraulic blade is vortex-shaped toward the outlet of the hydraulic impeller.

[0016] In some embodiments of this application, the pump body is provided with an outwardly extending water inlet pipe, the water inlet pipe is provided with a water inlet channel, the water inlet channel is connected to the water inlet through a conical surface, and the radial cross-sectional area of ​​the conical surface gradually increases from the inside to the outside; the pump body is provided with an outwardly extending water outlet pipe, the water outlet pipe is provided with a water outlet channel, the water outlet channel is connected to the water outlet, and the radial cross-sectional area of ​​the water outlet channel gradually increases from the inside to the outside.

[0017] In some embodiments of this application, the rear cover plate is provided with an mounting sleeve, which is connected to the pump shaft; the pump shaft is provided with a step, and a bushing is fitted on the pump shaft, with one end of the bushing abutting against the mounting sleeve and the other end abutting against the step; a mechanical seal is used between the pump cover and the bushing.

[0018] In some embodiments of this application, the pump cover is provided with a second cavity, which is connected to the first cavity through a pressure relief hole.

[0019] In some embodiments of this application, the wind turbine includes wind turbine blades and a connecting sleeve, with the inner side of the wind turbine blades connected to the connecting sleeve, and the connecting sleeve connected to the pump shaft.

[0020] In some embodiments of this application, a bearing housing is provided between the pump cover and the wind turbine impeller. One end of the bearing housing is connected to the pump cover, and the other end is provided with a bearing cover. The bearing cover and the bearing housing are detachably connected. A third opening is provided on the bearing cover, and the pump shaft passes through the third opening. A bearing is provided between the pump shaft and the bearing housing, and both sides of the bearing abut against the pump shaft and the bearing housing, respectively. An outwardly extending mounting foot is provided on the pump body.

[0021] In some embodiments of this application, the diameter D of the hydraulic impeller outlet is... j =54.9mm, diameter of the rear cover plate D2=265mm, width of the hydraulic impeller inlet b2=8mm, inlet angle of the first hydraulic blade β2=31°, outlet angle of the first hydraulic blade β1=31°, and eight first hydraulic blades are provided.

[0022] In some embodiments of this application, the pump body is a volute, the first cavity is a volute chamber, the base circle diameter of the first cavity is D3=275mm, and the inlet width of the first cavity is b3=8mm; a tongue is provided inside the first cavity, and the placement angle of the tongue is... =25°. Attached Figure Description

[0023] Figure 1 This is a schematic diagram of the structure of Embodiment 1 of the present invention;

[0024] Figure 2 This is a cross-sectional view of Embodiment 1 of the present invention;

[0025] Figure 3 yes Figure 2 A cross-sectional view along the AA direction;

[0026] Figure 4 This is a schematic diagram of the structure of the hydraulic impeller in Embodiment 1 of the present invention;

[0027] Figure 5 This is a cross-sectional view of the hydraulic impeller of Embodiment 1 of the present invention;

[0028] Figure 6 This is a cross-sectional view of the pump body according to Embodiment 1 of the present invention;

[0029] Figure 7 This is a cross-sectional view of the volute of Embodiment 1 of the present invention;

[0030] Figure 8 This is Example 1 of the present invention with a flow rate of 30m³. 3 Pressure distribution contour map of the intermediate section under the condition of / h;

[0031] Figure 9 This is Example 1 of the present invention at a flow rate of 25m³. 3 Pressure distribution contour map of the intermediate section under the condition of / h;

[0032] Figure 10 This is Example 1 of the present invention with a flow rate of 30m³. 3 Velocity streamline diagram of the intermediate section at / h;

[0033] Figure 11 This is Example 1 of the present invention at a flow rate of 25m³. 3 Velocity streamline diagram of the intermediate section at / h;

[0034] Figure 12 This is Example 1 of the present invention with a flow rate of 30m³. 3 Velocity distribution contour map of the intermediate section under the condition of / h;

[0035] Figure 13 This is Example 1 of the present invention at a flow rate of 25m³. 3 Velocity distribution contour map of the intermediate section under the condition of / h;

[0036] Figure 14 This is the external characteristic curve of Embodiment 1 of the present invention at 1500 r / min.

[0037] In the diagram: 1. Pump body; 2. First chamber; 3. First opening; 4. Inlet; 5. Outlet; 6. Pump cover; 7. Hydraulic impeller; 8. Pump shaft; 9. Wind turbine impeller; 10. Second opening; 11. Front cover plate; 12. Rear cover plate; 13. Hydraulic impeller outlet; 14. First hydraulic blade; 15. Hydraulic impeller inlet; 16. Pressure relief hole; 17. Water guide groove; 18. Second hydraulic blade; 19. Inlet pipe; 20. 21. Inlet channel; 22. Conical surface; 23. Outlet pipe; 24. Outlet channel; 25. Mounting sleeve; 26. Step; 27. Bushing; 28. Second cavity; 29. ​​Wind turbine blade; 30. Connecting sleeve; 31. Bearing housing; 32. Bearing cover; 33. Third opening; 34. Bearing; 35. Mounting foot; 36. Stationary ring assembly; 37. Dynamic ring assembly; 38. Inlet flange; 39. Outlet flange; 30. Tongue. Detailed Implementation

[0038] To further illustrate the technical means and effects of the present invention in achieving its intended purpose, the following detailed description of the specific implementation methods, structures, features, and effects of the present invention, in conjunction with the accompanying drawings and preferred embodiments, is provided below.

[0039] Example 1:

[0040] This embodiment provides a centrifugal hydraulic fan, such as Figures 1-5 As shown, it includes:

[0041] The pump body 1 has a first cavity 2 with a circular cross-section. The first cavity 2 has a first opening 3 in the axial direction. The cavity wall of the first cavity 2 has an inlet 4 and an outlet 5.

[0042] Pump cover 6 is used to block the first opening 3 and is detachably connected to pump body 1;

[0043] The hydraulic impeller 7 is rotatably mounted in the first cavity 2 and arranged coaxially with the first cavity 2;

[0044] Pump shaft 8 is connected to hydraulic impeller 7;

[0045] The wind turbine impeller 9 is connected to the pump shaft 8;

[0046] The pump cover 6 has a second axial opening 10, through which the pump shaft 8 passes. The hydraulic impeller 7 includes a front cover plate 11 and a rear cover plate 12. The center of the front cover plate 11 has a hydraulic impeller outlet 13, which is connected to the water outlet 5. A plurality of first hydraulic blades 14 are provided between the front cover plate 11 and the rear cover plate 12. A hydraulic impeller inlet 15 is formed between the front cover plate 11 and the rear cover plate 12, which is connected to the water inlet 4. The rear cover plate 12 has a pressure relief hole 16, which is used to balance the pressure on both sides of the rear cover plate 12.

[0047] The design of the pressure relief hole 16 allows water to flow from one side of the rear cover plate 12 through the pressure relief hole 16 to the other side of the rear cover plate 12, ensuring that the pressure on both sides of the rear cover plate 12 remains balanced, reducing the lateral pressure on the hydraulic impeller 7, thereby reducing the rotational resistance of the hydraulic impeller 7 and improving working efficiency.

[0048] To ensure reliable water intake, a water guide channel 17 is provided on the first cavity 2. The water guide channel 17 is arranged around the cavity wall of the first cavity 2. The top opening of the water guide channel 17 is connected to the first cavity 2. The width of the top opening of the water guide channel 17 is the same as the width of the hydraulic impeller inlet 15, so that most of the water flow is used to drive the hydraulic impeller 7, making its energy utilization rate of water flow high. The inlet 4 is connected to the water guide channel 17. The cross-sectional area of ​​the water guide channel 17 gradually decreases from the outside to the inside, so that the water flow velocity from the top opening of the water guide channel 17 is high, increasing the driving force on the hydraulic impeller 7. The cross-sectional area of ​​the water guide channel 17 gradually decreases along the circumference of the first cavity 2, and the cross-sectional area at the connection between the water guide channel 17 and the inlet 4 is the largest, ensuring the water flow velocity at the end of the water guide channel 17, so that the water flow from the end of the water guide channel 17 also has a driving force on the hydraulic impeller 7. The design of the water guide channel 17 ensures that the water flowing in from the inlet 4 first enters the water guide channel 17. The water guide channel 17 guides the water flow to flow around the cavity wall of the first cavity 2. At the same time, some water flows out from the top opening of the water guide channel 17 to drive the hydraulic impeller 7 to rotate. In other words, the water flow pushes the hydraulic impeller 7 in a circumferential direction, with a large pushing range and balanced pushing force.

[0049] To ensure reliable water intake, the water inlet 4 is tangent to the bottom of the water guide trough 17, ensuring smooth water intake. The water inlet 4 is located above the center of the hydraulic impeller 7, so that the incoming water will also flow downwards, utilizing gravitational potential energy. The highest point of the hydraulic impeller inlet 15 is higher than the lowest point of the water inlet 4.

[0050] For the hydraulic impeller 7 to be reliable, the first hydraulic blade 14 is arranged perpendicularly to the front cover plate 11, and the first hydraulic blade 14 extends from the outermost edge of the front cover plate 11 or the outermost edge of the rear cover plate 12 towards the center; the plurality of first hydraulic blades 14 are arranged in a vortex shape towards the hydraulic impeller outlet 13. In this embodiment, the front cover plate 11 and the rear cover plate 12 have the same diameter, that is, the first hydraulic blade 14 extends from the outermost edge of the front cover plate 11 and the rear cover plate 12 towards the center.

[0051] To ensure the reliability of the hydraulic impeller 7, a second hydraulic blade 18 is provided between adjacent first hydraulic blades 14. The second hydraulic blade 18 extends from the outermost side of the front cover plate 11 or the outermost side of the rear cover plate 12 toward the center. The second hydraulic blade 18 is vortex-shaped toward the hydraulic impeller outlet 13.

[0052] To ensure reliable water intake, the pump body 1 is equipped with an outwardly extending inlet pipe 19, on which an inlet channel 20 is provided. The inlet channel 20 is connected to the inlet 4 via a conical surface 21, the radial cross-sectional area of ​​which gradually increases from the inside to the outside. The cross-sectional area of ​​the inlet channel 20 is larger than that of the inlet 4, ensuring the water flow rate. The design of the conical surface 21 increases the inlet pressure and enhances the driving force of the water flow on the hydraulic impeller 7.

[0053] To ensure reliable water output, the pump body 1 is equipped with an outwardly extending outlet pipe 22, which has an outlet channel 23 connected to the outlet 5. The radial cross-sectional area of ​​the outlet channel 23 gradually increases from the inside to the outside. The cross-sectional area of ​​the outlet channel 23 is larger than that of the outlet 5 to ensure the water flow rate.

[0054] In this embodiment, the outer end of the water inlet pipe 19 is provided with an inlet flange 37, which can be easily connected to an external water inlet pipe; the outer end of the water outlet pipe 22 is provided with an outlet flange 38, which can be easily connected to an external water outlet pipe.

[0055] To ensure the reliability of the rear cover plate 12, an mounting sleeve 24 is provided on the rear cover plate 12, which is connected to the pump shaft 8. A step 25 is provided on the pump shaft 8, and a bushing 26 is fitted onto the pump shaft 8. One end of the bushing 26 abuts against the mounting sleeve 24, and the other end abuts against the step 25. A mechanical seal is used between the pump cover 6 and the bushing 26. Specifically, the mechanical seal includes a stationary ring assembly 35 and a rotating ring assembly 36. The stationary ring assembly 35 is connected and fixed to the pump cover 6 and is fitted onto the bushing 26. The rotating ring assembly 36 is located between the stationary ring assembly 35 and the rear cover plate 12 and is fitted onto the bushing 26. This mechanical seal provides good sealing performance.

[0056] For ease of installation, the pump cover 6 is provided with a second cavity 27, which is connected to the first cavity 2 through a pressure relief hole 16. The second cavity 27 is used to install a mechanical seal to ensure a reliable connection and seal between the pump shaft 8 and the pump cover 6; the pressure relief hole 16 is connected to the second cavity 27 to ensure the pressure relief effect of the pressure relief hole 16.

[0057] To ensure the reliability of the wind turbine impeller 9, the wind turbine impeller 9 includes wind turbine blades 28 and a connecting sleeve 29. The inner side of the wind turbine blades 28 is connected to the connecting sleeve 29, and the connecting sleeve 29 is connected to the pump shaft 8. The wind turbine blades 28 are used to rotate and generate wind power.

[0058] For reliable connection, a bearing housing 30 is provided between the pump cover 6 and the impeller 9. One end of the bearing housing 30 is connected to the pump cover 6, and the other end is provided with a bearing cover 31. The bearing cover 31 is detachably connected to the bearing housing 30. The bearing cover 31 has a third opening 32, through which the pump shaft 8 passes. A bearing 33 is provided between the pump shaft 8 and the bearing housing 30, with both sides of the bearing 33 abutting against the pump shaft 8 and the bearing housing 30 respectively. The pump body 1 is provided with outwardly extending mounting feet 34. The design of the bearing housing 30 improves protection and prevents foreign objects from entering and contacting the pump shaft 8. The design of the bearing 33 makes the rotation of the pump shaft 8 smoother, and the bearing housing 30 supports the bearing 33, thereby supporting the pump shaft 8. The mounting feet 34 facilitate installation.

[0059] In this embodiment, the rated design parameters of the centrifugal hydraulic fan are shown in Table 1 below:

[0060] Table 1

[0061] flow Maximum recovery head rotational speed Shaft power Maximum outer diameter Design pressure medium 28m³ / h <90 m 1500 r / min 2.5kW 805mm 4Mpa 25° clean water

[0062] The inlet pipe diameter of the water inlet channel 20 is 80mm, and the outlet pipe diameter of the water outlet channel 23 is 80mm.

[0063] The diameter D of the hydraulic impeller outlet 13 j Determination: Calculate the effective diameter D0 of the impeller inlet, and take Q = 28m. 3 / h, n=1500 rpm, K0=3.9, we get:

[0064]

[0065]

[0066] Where d h Let be the impeller hub diameter. We will ignore the hub diameter here and set it to 0, resulting in:

[0067]

[0068] Determining the diameter D2 of the rear cover plate 12:

[0069]

[0070] Where K D Taking 15.3, we get:

[0071]

[0072] Determining the width b2 of the hydraulic impeller inlet 15:

[0073]

[0074] Where k b Taking 0.46, we get:

[0075]

[0076] Let b2 = 8mm.

[0077] The inlet angle β2 of the first hydraulic blade 14 is set to 31°, and the outlet angle β1 of the first hydraulic blade 14 is set to 31°.

[0078] Determining the number of blades Z of the hydraulic impeller 7:

[0079]

[0080] Where R2-R1 is the unfolded length of the centerline within the axial projection of the impeller flow channel. It is the radius of the centroid of the center line. It is the average value of the blade inlet and outlet angles, and K is an empirical coefficient, which is taken as K=4.4 here.

[0081] Based on the known parameters, we can derive: R2-R1=0.0583m, R2+R1=0.2067m.

[0082]

[0083] The first hydraulic blade 14 has eight blades, and the second hydraulic blade 18 has eight blades. The maximum thickness of the first hydraulic blade 14 and the second hydraulic blade 18 is 6.1 mm.

[0084] like Figure 6 As shown, in this embodiment, the pump body 1 is a volute, the first cavity 2 is a volute chamber; the first cavity 2 is provided with a tongue 39; the water inlet pipe 19 is a volute chamber contraction pipe.

[0085] The cross-sectional shape of the volute can be rectangular, pear-shaped, trapezoidal, or circular. The cross-sectional shape of the volute has little impact on performance and can be selected based on structural and manufacturing convenience. In this embodiment, a trapezoidal volute is used.

[0086] For ease of calculation and drawing, such as Figure 7 As shown, the volute is typically divided into eight sections at 45° angles to each other, meaning the volute is cut using eight axial planes to determine the shape and area of ​​each section. During design, the eighth section is calculated first, and the other sections are determined based on this eighth section.

[0087] The circle tangent to the starting point of the helix at section 8 (or to the head of the tongue 39) is called the base circle. There should be a certain clearance between the base circle and the hydraulic impeller 7. If this clearance is too small, it can easily cause noise and vibration due to fluid flow blockage. If the clearance is too large, it can reduce the non-uniformity of the flow around the guide vane, reduce noise and vibration, and slightly improve efficiency. In this embodiment, the base circle diameter of the first cavity 2 is D3 = 275 mm.

[0088] The inlet width b3 of the first cavity 2 is usually greater than the width b2 of the hydraulic impeller inlet 15. Usually b3 = b2 + (5~10). In this embodiment, the inlet width of the first cavity 2 is b3 = 8mm.

[0089] The tongue 39 is located at or slightly shortly after the beginning of the spiral section of the vortex chamber, separating the spiral section from the contraction tube. The section passing through the head of the tongue 39 is conventionally called the 0 section, and the angle between the tongue 39 and the 8th section is called the tongue placement angle. express. The size should ensure a smooth connection between the spiral section and the contraction tube, and minimize the radial dimension as much as possible. In this embodiment, the placement angle of the tongue 39 is taken as... =25°.

[0090] The outlet of the contraction tube can be approximated as the 8th section of the volute. The main structural parameters of the contraction tube are: the suction inlet diameter D of the inlet pipe 19. d =50mm, the height L of the water inlet pipe 19 is 345mm, and the diffusion angle θ of the water inlet pipe 19 is 7°~13°.

[0091] In this embodiment, the developed hydraulic turbine has a specific speed of only 20, which is an ultra-low specific speed type.

[0092] like Figure 8 , Figure 9 As shown, at a flow rate of 30m³ 3 / h and flow rate 25m 3 No obvious high-pressure zone was observed in the hydraulic impeller 7 area at both operating points / h, and the pressure distribution was uniform throughout the flow area.

[0093] like Figure 10 , Figure 11 As shown, at a flow rate of 30m³ 3 / h and flow rate 25m 3 The velocity streamline distribution inside the pump body 1 and the inlet pipe 19 is very uniform under both operating conditions, while the velocity streamline distribution inside the hydraulic impeller 7 is not uniform enough. This is due to the dynamic and static interference between the pump body 1 and the hydraulic impeller 7 at the inlet section of the hydraulic impeller 7.

[0094] like Figure 12 , Figure 13 As shown, due to the interference of static and dynamic forces, a non-uniform flow field can still be observed inside the hydraulic impeller 7. Because the designed hydraulic turbine has an ultra-low specific speed, the width of the hydraulic impeller outlet 13 is small, and high-pressure fluid can also be observed at each section of the pump body 1. However, the flow field inside the hydraulic impeller 7 is relatively uniform overall, thus ensuring that the flow condition inside the turbine is more stable.

[0095] Table 2 shows the theoretically calculated values ​​of the axial force on the hydraulic turbine under different operating conditions. As can be seen from the table, within a given flow range, the axial force on the hydraulic impeller 7 first increases to a maximum of 443.68 N at approximately 28 cubic meters per second, and then decreases to 328.55 N at 33.6 cubic meters per second. This decrease is related to the angle at which the liquid flows out of the hydraulic impeller 7. Through comparison with theoretical formulas and calculations, the axial force on the hydraulic impeller 7 is very small, having minimal impact on the turbine's operation and solving the problem of unstable operation at ultra-low specific speeds.

[0096] Table 2

[0097] Traffic Q / / h 22.4 28 33.6 F / N 305.558 443.68 328.55

[0098] Table 3 shows the CFD calculation results of the turbine's efficiency, shaft power, and recovery head at different flow rates under a flow rate of 1500 r / min. Figure 14 It can be seen that the developed turbine, within the given parameter range, has a performance of 25m 3 / h to 30m 3 Within a range of / h, its output power fully meets the shaft power required to drive the wind turbine rotor 9, while its theoretically predicted efficiency is high within the turbine operating range, overcoming the difficulty of a narrow high-efficiency range in ultra-low specific speed hydraulic turbines. 28m 3 Although the power output is less than 2.5kW per hour, the wind turbine rotor 9 only requires 2.2kW of power to operate normally, and this single-stage hydraulic turbine can fully meet the operating requirements.

[0099] Table 3

[0100]

[0101] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention in any way. Although the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art can make some modifications or alterations to the above-disclosed technical content to create equivalent embodiments without departing from the scope of the present invention. Any simple modifications, equivalent changes and alterations made to the above embodiments based on the technical essence of the present invention without departing from the scope of the present invention shall still fall within the scope of the present invention.

Claims

1. A centrifugal water power fan, characterized by, The utility model relates to a pump, comprising: a pump body (1) provided with a first cavity (2) with a circular cross section, the first cavity (2) being provided with an axial first opening (3), the cavity wall of the first cavity (2) being provided with a water inlet (4) and a water outlet (5); a pump cover (6) for plugging the first opening (3) and detachably connected with the pump body (1); a hydraulic impeller (7) rotatably arranged in the first cavity (2) and coaxially arranged with the first cavity (2); a pump shaft (8) connected with the hydraulic impeller (7); a wind power impeller (9) connected with the pump shaft (8); the pump cover (6) is provided with an axial second opening (10), and the pump shaft (8) penetrates through the second opening (10); the hydraulic impeller (7) comprises a front cover plate (11) and a rear cover plate (12), the center of the front cover plate (11) is provided with a hydraulic impeller outlet (13), the hydraulic impeller outlet (13) is communicated with the water outlet (5), a plurality of first hydraulic blades (14) are arranged between the front cover plate (11) and the rear cover plate (12), a hydraulic impeller inlet (15) is formed between the front cover plate (11) and the rear cover plate (12), the hydraulic impeller inlet (15) is communicated with the water inlet (4), the rear cover plate (12) is provided with a pressure relief hole (16) for balancing the pressure on both sides of the rear cover plate (12); the diameters of the front cover plate (11) and the rear cover plate (12) are the same; the first cavity (2) is provided with a water guide groove (17) arranged around the cavity wall of the first cavity (2), the top of the water guide groove (17) is open and communicated with the first cavity (2), the top opening width of the water guide groove (17) is the same as the width of the hydraulic impeller inlet (15), the water inlet (4) is communicated with the water guide groove (17); the first hydraulic blades (14) are arranged perpendicularly to the front cover plate (11), and the first hydraulic blades (14) extend from the outermost side of the front cover plate (11) or the outermost side of the rear cover plate (12) to the center; a plurality of first hydraulic blades (14) are in a spiral shape towards the hydraulic impeller outlet (13); second hydraulic blades (18) are arranged between adjacent first hydraulic blades (14) and extend from the outermost side of the front cover plate (11) or the outermost side of the rear cover plate (12) to the center; the second hydraulic blades (18) are in a spiral shape towards the hydraulic impeller outlet (13); the diameter D2 of the rear cover plate (12) is 265 mm; the base circle diameter D3 of the first cavity (2) is 275 mm.

2. A centrifugal hydraulic fan as claimed in claim 1, characterized in that: The cross-sectional area of the water guide groove (17) gradually decreases from outside to inside; the cross-sectional area of the water guide groove (17) gradually decreases along the circumference of the first cavity (2), and the cross-sectional area of the water guide groove (17) at the connection with the water inlet (4) is the largest.

3. A centrifugal hydraulic fan as claimed in claim 2, characterized in that: The water inlet direction of the water inlet (4) is tangent to the groove bottom of the water guide groove (17); the water inlet (4) is located above the center of the hydraulic impeller (7); the highest point of the hydraulic impeller inlet (15) is higher than the lowest point of the water inlet (4).

4. A centrifugal hydraulic fan as claimed in claim 1, characterized in that: The pump body (1) is provided with an outwardly extending water inlet pipe (19), the water inlet pipe (19) is provided with a water inlet channel (20), the water inlet channel (20) is communicated with the water inlet (4) through a conical surface (21), the conical surface (21) gradually increases in the radial cross-sectional area from inside to outside; the pump body (1) is provided with an outwardly extending water outlet pipe (22), the water outlet pipe (22) is provided with a water outlet channel (23), the water outlet channel (23) is communicated with the water outlet (5), and the water outlet channel (23) gradually increases in the radial cross-sectional area from inside to outside.

5. A centrifugal hydraulic fan as claimed in claim 1, characterized in that: The pump cover (6) is provided with a second cavity (27), and the second cavity (27) is communicated with the first cavity (2) through the pressure relief hole (16).

6. A centrifugal hydraulic fan as claimed in claim 1, characterized in that: The pump cover (6) and the wind wheel (9) are provided with a bearing box (30), one end of the bearing box (30) is connected with the pump cover (6), the other end is provided with a bearing cover (31), the bearing cover (31) is detachably connected with the bearing box (30), the bearing cover (31) is provided with a third opening (32), and the pump shaft (8) is arranged on the third opening (32); the pump shaft (8) and the bearing box (30) are provided with a bearing (33), and the two sides of the bearing (33) are respectively abutted with the pump shaft (8) and the bearing box (30); the pump body (1) is provided with an outwardly extending mounting foot (34).

7. A centrifugal hydraulic fan as claimed in claim 1, characterized in that: The diameter D of the water turbine outlet (13) j = 54.9 mm; the width b2 of the water turbine inlet (15) = 8 mm; the inlet angle β2 of the first water turbine blade (14) = 31°; the outlet angle β1 of the first water turbine blade (14) = 31°; the first water turbine blade (14) is provided with eight pieces.

8. A centrifugal hydraulic fan as claimed in claim 1, characterized in that: The pump body (1) is a volute, and the first cavity (2) is a volute chamber; the inlet width b3 of the first cavity (2) is 8 mm; the first cavity (2) is provided with a partition tongue (39), and the setting angle of the partition tongue (39) is 25°. =25°.

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